US3435770A - Liquid fuel injection pumps - Google Patents

Liquid fuel injection pumps Download PDF

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Publication number
US3435770A
US3435770A US637208A US3435770DA US3435770A US 3435770 A US3435770 A US 3435770A US 637208 A US637208 A US 637208A US 3435770D A US3435770D A US 3435770DA US 3435770 A US3435770 A US 3435770A
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US
United States
Prior art keywords
plunger
control edge
liquid fuel
fuel injection
groove
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
US637208A
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English (en)
Inventor
Arthur J Ellis
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.)
Bryce Berger Ltd
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Bryce Berger Ltd
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Filing date
Publication date
Application filed by Bryce Berger Ltd filed Critical Bryce Berger Ltd
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Publication of US3435770A publication Critical patent/US3435770A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the piston

Definitions

  • a liquid fuel pump including a plunger which has a groove therein that defines a control edge for modifying the rate of pressure decay, said groove being less in depth at a point immediately adjacent the control edge than it is at a point remote from said edge.
  • This invention relates to liquid fuel injection pumps of the type for supplying fuel to the combustion chamber of an internal combustion engine through a conduit to a nozzle valve and comprising a plunger reciprocably mounted within a cylinder with means for imparting a constant stroke to the plunger, the plunger and cylinder bore defining a pumping chamber, at least one outlet from the pumping chamber, a delivery valve at said outlet, at least one port (formed in the' wall of the cylinder) and at least one complementary groove on the peripheral surface of the plunger including a longitudinally shaped control edge, the groove below the control edge being in continuous communication with the pumping chamber, the said control edge being generally helical in shape and arranged to register with the said port during a pumping stroke thereby to terminate the delivery of fuel from the pumping chamber by release of pressure from the pumping chamher, the resultant rate of pressure decay in the system being a function of several factors such as the minimum flow area at any point downstream of the pumping chamher, the dimensions and rate of closure of the delivery valve and the dimensions and rate of
  • the present invention is based on the aforesaid appreciation and upon the conception of new means for controlling the rate, as well as the timing, of pressure, decay without the same control limitations at present existing as regards shape and size of ports and the complementary groove or other escape means.
  • the object of the present invention is to provide im- "ice proved means for modifying the rate of pressure decay.
  • a liquid fuel pump of the kind referred to is characterised in that the cross section of the groove is such that its radial depth immediately adjacent to the control edge is less than its radial depth at another point more remote from such edge.
  • the pump aforesaid may be further characterised in that the control edge is formed on the plunger by a groove and rebate therein defining primary and secondary control edges; or further characterised in that the said two edges are parallel to each other; or further characterised in that the radial depth of the rebate adjacent to the primary control edge increases progressively towards or away from such edge; or further characterised in that the primary and secondary control edges are not parallel to each other.
  • FIG. 1 is a longitudinal section of one example of the invention
  • FIGS. 2a, 2b, 2c and 2d are fragmentary cross-section on line A-A of FIG. 1;
  • FIGS. 3 and 4 are side elevations showing the upper ends of alternative forms of plunger
  • FIG. 5 is a part longitudinal section of a cylinder and plunger of alternative form providing hydraulic pressure balance about the plunger.
  • FIG. 1 shows a pump cylinder 10, with diametrically opposed ports 17, a pump plunger 11 located therein, a delivery valve 12, and conduit 16, with the usual control edge 13 formed on the plunger by a helical groove 14, in continuous communication with the space above the plunger via a longitudinal groove 15, the control edge being shown in a modified form in accordance with the invention and parallel to the helical groove.
  • the pump plunger is constructed at its outer end in conventional manner with a head 11a complementary to an actuating cam (not shown) and with a toothed segment 11b complementary to a toothed control rack (not shown). Conventional spring return gears (not shown) is provided for the plunger.
  • the shape of the modified form may be in accordance with the cross-sections in FIG. 2(a) as a constant depth rebate providing substantially two defined edges 18 and 19 respectively primary and secondary edges.
  • FIG. 2( b) Another alternate form is shown in FIG. 2( b) as a sloping rebate of greatest depth adjacent to the primary control edge 21; or FIG. 2(0) as a sloping rebate of least depth adjacent to the primary control edge 22; or 2(d) as a rebate of progressively varying depth of least depth adjacent to the primary control edge 23.
  • FIG. 3 shows a pump plunger in accordance with the invention having a rebate at the primary control edge of any of the forms shown in FIG.
  • FIG. 4 shows a pump plunger similarly in accordance with the invention and with a rebate of progressively decreasing width having its least width at that end of the control edge determining the largest pump delivery stroke.
  • two or more escape means may be provided around the periphery of the plunger, each with a control edge coacting simultaneously with separate ports in the cylinder.
  • the modifications herein described may be incorporated at any one or all of these control edges and provided that at least two such escape means are provided, one of said escape means may be of a conventional radial depth, the other being of the modified radial depth and position in accordance with the invention and not acting simultaneously with the other escape means and their coacting ports but still giving an effective degree of hydraulic balance.
  • An example of this is as shown in the drawing 3 FIG.
  • the cylinder 50 having two diametrically opposed ports 52, and the plunger 51, having one control edge 53, provided by an escape groove of conventional radial depth and position, the other control edge 54 being provided by a second escape groove having its radial depth and position in accordance with the invention.
  • the longitudinal groove referred to in the above description may be replaced by a relieved area, or spill passage, or a drilled hole while the converse construction is also included, i.e. the control edge or edges could be formed in the cylinder and the complementary port or ports in the plunger.
  • the relative rotational adjustment could also be applied to the cylinder instead of, or in addition to, such movement of the plunger and in that case the two adjustments could be efiected as a function of different factors.
  • a pump generally in accordance with the illustration FIG. 1, operating at 214 strokes per min. having a plunger stroke of 22 mm. and plunger diameter 24 mm., a delivery valve of 250 cubic mm. unloading volume, delivering 3750 cubic mm. of liquid fuel at a peak pressure of approximately 650 kgm./sq. cm. having two ports 6 mm. diameter in the cylinder coacting with two conventional helical escape grooves in the plunger periphery each being 2.5 mm. deep and 6.35 mm. Wide in a plane normal to the control edge formed by each groove, one control edge being modified in accordance with the invention as illustrated by FIG. 2a, the rebate formed being 0.25 mm. deep and 2.22 mm. wide in a plane normal to the primary control edge thus formed.
  • Such proportions were found to be effective to eliminate or sustantially reduce gas blow-back at a nozzle valve having a theoretical valve closure time of 0.57 millisecond.
  • a liquid fuel injection pump comprising a cylinder, a plunger reciprocably mounted therein, defining a pumping chamber at one end thereof, means for imparting reciprocation at a constant stroke to said plunger, at least one delivery outlet from said chamber, a delivery -valve at said outlet, at least one port and complementary groove defining a control edge at the inner surface of the cylinder and periphery of the plunger in continuous communication with the pumping chamber, the said control edge being generally helical in shape, means for effecting relative rotational positioning of the plunger and cylinder to adjust the timing of relative register in the reciprocal movement of the plunger to adjust the pump output for each stroke, characterised in that the cross section of the groove is such that its radial depth immediately adjacent to the control edge is less than its radial depth at another point more remote from such edge.
  • a liquid fuel injection pump according to claim 1 further characterised in that the control edge is formed on the plunger by a groove and rebate therein defining primary and secondary control edges.
  • a liquid fuel injection pump according to claim 2 further characterised in that the said two edges are parallel.
  • a liquid fuel injection pump according to claim 2. further characterised in that the radial depth of the rebate decreases progressively away from the primary control edge up to the secondary edge.
  • a liquid fuel injection pump according to claim 2 further characterised in that the radial depth of the rebate adjacent to the primary control edge increases progressively away from the primary control edge up to the secondary edge.
  • a liquid fuel injection pump according to claim 2 further characterised in that the primary and secondary control edges are parallel to each other.
  • a liquid fuel injection pump according to claim 2 further characterised in that the primary and secondary control edges are not parallel to each other.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)
US637208A 1966-05-10 1967-05-09 Liquid fuel injection pumps Expired - Lifetime US3435770A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB2063266 1966-05-10
GB18152/67A GB1159005A (en) 1966-05-10 1966-05-10 Liquid Fuel Injection Pumps.
GB9358/68A GB1249304A (en) 1966-05-10 1968-02-27 Liquid fuel injection pumps
NL6804800A NL6804800A (nl) 1966-05-10 1968-04-05 Brandstofinjectiepomp

Publications (1)

Publication Number Publication Date
US3435770A true US3435770A (en) 1969-04-01

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ID=27447712

Family Applications (2)

Application Number Title Priority Date Filing Date
US637208A Expired - Lifetime US3435770A (en) 1966-05-10 1967-05-09 Liquid fuel injection pumps
US801952A Expired - Lifetime US3552889A (en) 1966-05-10 1969-02-25 Liquid fuel injection pumps

Family Applications After (1)

Application Number Title Priority Date Filing Date
US801952A Expired - Lifetime US3552889A (en) 1966-05-10 1969-02-25 Liquid fuel injection pumps

Country Status (6)

Country Link
US (2) US3435770A (fr)
CH (2) CH456246A (fr)
DE (2) DE1576466A1 (fr)
FR (2) FR1523646A (fr)
GB (2) GB1159005A (fr)
NL (1) NL6804800A (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1283343A (en) * 1968-11-08 1972-07-26 Lucas Industries Ltd Liquid fuel injection pumps
DE2151884A1 (de) * 1971-10-19 1973-04-26 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
CH601662A5 (fr) * 1975-11-05 1978-07-14 Semt
DE2730091C2 (de) * 1977-07-02 1986-12-04 Robert Bosch Gmbh, 7000 Stuttgart Schrägkantengesteuerte Kraftstoffeinspritzpumpe für Brennkraftmaschinen
AT388214B (de) * 1983-02-17 1989-05-26 Steyr Daimler Puch Ag Kraftstoff-einspritzaggregat fuer je einen zylinder eines dieselmotors
GB2135395B (en) * 1983-02-14 1987-03-18 Steyr Daimler Puch Ag Fuel-injection unit for each cylinder of a diesel engine
DE3804018A1 (de) * 1987-06-10 1989-08-24 Kloeckner Humboldt Deutz Ag Einspritzpumpe mit voreinspritzung
DE3804843A1 (de) * 1988-02-17 1989-08-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
GB2273320B (en) * 1992-12-08 1995-09-13 Lucas Ind Plc Fuel injection pump

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2211252A (en) * 1937-11-13 1940-08-13 Bendix Aviat Corp Valve for fuel pump mechanism
US2348282A (en) * 1941-05-01 1944-05-09 Bendix Aviat Corp Fuel injection apparatus
US2612842A (en) * 1946-11-13 1952-10-07 Worthington Corp Fuel injection pump
US2696786A (en) * 1952-01-21 1954-12-14 Caterpillar Tractor Co Fuel injection pump plunger
US2740667A (en) * 1952-04-04 1956-04-03 Gen Motors Corp Compression operated fuel injector pump
US2890657A (en) * 1955-08-12 1959-06-16 Gen Motors Corp Unit injector pump with pilot injection
US3123006A (en) * 1964-03-03 Injector plunger
US3368491A (en) * 1966-06-22 1968-02-13 Murphy Diesel Company Fuel injection pump

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3123006A (en) * 1964-03-03 Injector plunger
US2211252A (en) * 1937-11-13 1940-08-13 Bendix Aviat Corp Valve for fuel pump mechanism
US2348282A (en) * 1941-05-01 1944-05-09 Bendix Aviat Corp Fuel injection apparatus
US2612842A (en) * 1946-11-13 1952-10-07 Worthington Corp Fuel injection pump
US2696786A (en) * 1952-01-21 1954-12-14 Caterpillar Tractor Co Fuel injection pump plunger
US2740667A (en) * 1952-04-04 1956-04-03 Gen Motors Corp Compression operated fuel injector pump
US2890657A (en) * 1955-08-12 1959-06-16 Gen Motors Corp Unit injector pump with pilot injection
US3368491A (en) * 1966-06-22 1968-02-13 Murphy Diesel Company Fuel injection pump

Also Published As

Publication number Publication date
DE1576466A1 (de) 1970-02-12
GB1159005A (en) 1969-07-23
FR2002695A1 (fr) 1969-10-31
NL6804800A (nl) 1969-10-07
CH456246A (de) 1968-05-15
FR1523646A (fr) 1968-05-03
GB1249304A (en) 1971-10-13
US3552889A (en) 1971-01-05
CH511370A (de) 1971-08-15
DE1909255A1 (de) 1969-09-11

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