US3552366A - Liquid fuel pumping apparatus - Google Patents

Liquid fuel pumping apparatus Download PDF

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Publication number
US3552366A
US3552366A US760195A US3552366DA US3552366A US 3552366 A US3552366 A US 3552366A US 760195 A US760195 A US 760195A US 3552366D A US3552366D A US 3552366DA US 3552366 A US3552366 A US 3552366A
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US
United States
Prior art keywords
piston
fluid pressure
servovalve
spring
bore
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
US760195A
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English (en)
Inventor
Kenneth Albert Walters Kemp
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.)
CAV Ltd
Original Assignee
CAV Ltd
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Filing date
Publication date
Application filed by CAV Ltd filed Critical CAV Ltd
Application granted granted Critical
Publication of US3552366A publication Critical patent/US3552366A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M41/1411—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 characterised by means for varying fuel delivery or injection timing
    • F02M41/1427—Arrangements for metering fuel admitted to pumping chambers, e.g. by shuttles or by throttle-valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—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
    • F02M41/1411—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 characterised by means for varying fuel delivery or injection timing
    • F02M41/1416—Devices specially adapted for angular adjustment of annular cam
    • 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
    • F02M2041/1438—Arrangements or details pertaining to the devices classified in F02M41/14 and subgroups
    • F02M2041/145—Throttle valves for metering fuel to the pumping chamber

Definitions

  • a liquid fuel pumping apparatus for supplying fuel to an internal combustion engine and including an injection pump including a member movable by a piston to vary the timing of injection of fuel, the piston containing a servovalve, one end of which is subjected to a first fluid pressure dependent upon the speed at which the apparatus is driven, and the other end of which is subjected to a second fluid pressure which varies in accordance with the load on the associated engine, the servovalve acting to control the fluid pressure applied to the piston.
  • This invention relates to liquid fuel pumping apparatus for supplying fuel to internal combustion engines and of the kind comprising in combination, an injection pump including a member adjustable to control the timing of injection of fuel to the engine, a fluid pressure operable piston for determining the setting of said member, a resiliently loaded servovalve for controlling the fluid pressure applied to said piston and means for applying to the servovalve in opposition to the force exerted by its spring, a first fluid pressure dependent upon the speed at which the apparatus is driven.
  • the object of the invention is to provide such an apparatus in a simple and convenient form.
  • an apparatus of the kind specified includes additional means to provide a second fluid pressure which is dependent upon the load applied to the engine, said second fluid pressure being applied to the servovalve to assist the action of the spring whereby the setting of the piston is depended upon the speed of and the load applied to the engine.
  • FIG. 1 is a sectional side elevation of one example of a liquid fuel pumping apparatus in accordance with the invention
  • FIG. 2 is a section on the line 2-2 of FIG. 1;
  • FIG. 3 is a sectional plan view to an enlarged scale of part of the apparatus of FIGS. 1 and 2;
  • FIG. 4 shows a fluid circuit diagram of the apparatus.
  • a body part 1 in which is mounted a rotary cylindrical distributor member 2 having formed at one end a head 3 in which is formed a transverse bore 4 mounting a pair of reciprocable pumping plungers 9.
  • the pumping plungers are arranged to be moved inwardly as the distributor member is rotated, by the action of a plurality of cam lobes formed on the internal periphery of an annular cam ring 15 which surrounds the distributor member at this point.
  • Also formed in the distributor member is a longitudinal bore which at one point is in communication with an outwardly extending delivery passage 17 which is arranged to register in turn and as the distributor member rotates, with a plurality of outlet ports 18 which in use, are connected to injection nozzles mounted on the associated engine.
  • the longitudinal passage is in communication with a plurality of equiangularly disposed and radially extending inlet passages 11 which register in turn, as the distributor member rotates with an inlet port 12 formed in the body part.
  • the communication between an inlet passage 11 and the inlet port 12 occurs during the time when the plungers 9 are permitted to move outwardly by the cam lobes and the communication of the delivery passage 17 with one of the outlet ports 18 occurs during inward movement of the plungers.
  • the rotor of a vane-type feed pump 5 having an inlet 6 and outlet 7 in the body part.
  • the inlet 6 of the feed pump is in use, connected to a-source of liquid fuel and the inlet and outlet are interconnected by way of valve means 8 which controls the output pressure of the feed pump in such a manner that it varies in accordance with the speed at which the apparatus is driven. Since the distributor member is driven by the engine, the output pressure of the feed pump is also dependent upon the speed at which the engine is driven.
  • the outlet of the feed pump is in communication with the aforesaid inlet port by way of a passage formed in the body part and this passage is provided with a throttle valve 14 whereby the quantity of fuel which flows through the inlet port 12 whilst the plungers are capable of moving outwardly can be varied.
  • the throttle valve consists of an angularly adjustable cylindrical member the setting of which is controlled by a speed-sensitive governor (not shown).
  • the cam ring 15 is angularly adjustable within the body part about the axis of rotation of the distributor member 2 and in this manner variation in the timing of injection of fuel to the engine can be efi'ected.
  • a fluid pressure operable piston 19 is provided for adjusting the setting of the cam ring and this is located within a cylinder 20 which is disposed tangentially relative to the cam ring.
  • the piston is connected to the cam ring by means of a radial peg secured to the latter and engaged within a recess formed in the piston.
  • the piston is loaded by means of a coiled compression spring 21 towards the retarded position.
  • a servovalve 23 Formed in the piston is an axially extending bore 22 in which is slidably mounted, a servovalve 23 having three spaced lands.
  • the servovalve is loaded in the same direction as the piston 19 by means of a coiled compression spring 24 one end of which bears upon the servovalve and the other end of which bears upon the base portion of a cup-shaped member 25 slidable within the bore 22 of the piston and urged by the action of the coiled compression spring 24 into contact with a plug 26 which closes the adjacent end of the chamber which contains the piston.
  • a passage 27 which extends from the end thereof remote from the coiled compression spring and which breaks into the bore containing the servovalve at a first port 28.
  • the first port 28 is closed by the center land 23a of the servovalve.
  • the groove on the side of the center land 230 which is remote from the coiled compression spring 24 is in communication by way of a passage 29 formed in the piston and a cooperating passage 30 in the surrounding body part, with fluid under pressure.
  • this fluid is derived from the outlet 7 of the feed pump although any other source of fluid under pressure may be utilized such for instance as the oil pump of the associated engine.
  • the groove on the opposite side of the center land 23a is in communication by way of a passage 31 formed within the piston and a passage 32 in the body part, with a drain.
  • This drain may be the usual drain which is to be found in this form of pumping apparatus or alternatively it may be the inlet of the feed pump.
  • the end of the chamber containing the spring which loads the piston is also in communication with the drain.
  • a further passage 33 formed in the piston and a cooperating passage 34 in the body part communicates with the outlet 7 of the feed pump so that the pressure of fuel delivered by the feed pump is applied to the end of the servovalve 23 to move it in opposition to the action of the coiled compression spring in operation, as the output pressure of the feed pump varies, the servovalve moves in the appropriate direction and the port 28 is uncovered to one or the other of the grooves of the servovalve. If the pressure is increasing the port 28 is uncovered to the groove which is in communication with the passage 29 and when this occurs fluid under pressure flows through the port and the piston is moved in opposition to the action of its spring. Eventually an equilibrium position is achieved in which the port 28 is again closed by the center land 23a.
  • the timing of injection of fuel to the engine should be varied in accordance with the load applied to the engine.
  • the load applied to the engine or in other words the power developed by the engine is dependent upon quantity of fuel supplied to the engine and this is determined by the setting of the throttle 14.
  • a passage 35 is provided in the piston 19 and this cooperates with a passage 36 in the body part.
  • the passage 35 breaks into the bore 22 containing the servovalve so that fluid pressure can act upon the servovalve to assist the action of the coiled compression spring 24.
  • acup-shaped part 24a is provided and which is slidable within the bore 22 relative to the piston 19.
  • the operation of the apparatus is exactly as described except that the servovalve is now responsive to two fluid pressures as well a as the force exerted by the coiled compression spring 24.
  • the pressure of fuel within the passage 35 is controlled as shown in FIG. 4 by a variable orifice 37 defined by the throttle .valve 14.
  • the fuel pressure upstream of the variable orifice is derived from the outlet of the feed pump and means is pro- ,vided for maintaining the pressure upstream of the variable orifice substantially constant.
  • this means may take the form of a restriction 38 disposed intermediate the variable orifice and the outlet of the feed pump and a constant pressure valve 39 for maintaining the pressure intermediate the restriction and the variable orifice, substantially constant.
  • the downstream side of the variable orifice is connected to the passage 36 and a restrictor 40 is provided in a branch passage which communicates with the drain. Adjustment of the throttle varies the effective size of the variable orifice and thereby ,the pressure which is applied through to the servovalve.
  • a liquid fuel pumping apparatus for supplying fuel to infinal combustions and comprising an injection pump, a member adjustable to control the timing of injection of fuel to thexngine, a fluid pressure operable piston contained within a cylinder, means connecting said piston to said member so that movement of the piston will efi'ect adjustment of said member, an end closure for the cylinder, a coiled compression spring acting between the piston and said end closure, said spring acting to urge the piston towards one end of the cylinder, a bore formed in said piston, a servovalve slidable in said bore for controlling the fluid pressure applied to the piston at its end remote from its spring, a further spring acting on the servovalve, passage means through which a first fluid pressure can be admitted to the bore so as to act on the servovalve in opposition to its spring, the magnitude of said first fluid pres sure being dependent upon the speed at which the apparatus is driven, a part slidable in the open end at the bore and which is loaded against said end closure by the

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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)
US760195A 1967-09-22 1968-09-17 Liquid fuel pumping apparatus Expired - Lifetime US3552366A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB4323267 1967-09-22

Publications (1)

Publication Number Publication Date
US3552366A true US3552366A (en) 1971-01-05

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ID=10427844

Family Applications (1)

Application Number Title Priority Date Filing Date
US760195A Expired - Lifetime US3552366A (en) 1967-09-22 1968-09-17 Liquid fuel pumping apparatus

Country Status (4)

Country Link
US (1) US3552366A (de)
DE (1) DE1776101B1 (de)
FR (1) FR1580052A (de)
GB (1) GB1238283A (de)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3869226A (en) * 1972-09-12 1975-03-04 Cav Ltd Fuel pumping apparatus
US3897764A (en) * 1973-05-18 1975-08-05 Cav Ltd Liquid fuel injection pumping apparatus
US3943902A (en) * 1973-07-13 1976-03-16 C. A. V. Limited Fuel injection pumping apparatus
US4050437A (en) * 1975-04-01 1977-09-27 Cav Limited Liquid fuel injection pumping apparatus
US4074667A (en) * 1974-07-19 1978-02-21 C.A.V. Limited Liquid fuel injection pumping apparatus
US4080109A (en) * 1975-07-05 1978-03-21 Lucas Industries Limited Fuel injection pumping apparatus
US4176640A (en) * 1976-04-20 1979-12-04 Lucas Industries, Limited Fuel injection pumping apparatus
US4365939A (en) * 1979-07-06 1982-12-28 Lucas Industries Limited Fuel injection pumping apparatus
US4366795A (en) * 1979-08-07 1983-01-04 Robert Bosch Gmbh Fuel injection pump for internal combustion engine
US4373492A (en) * 1979-08-07 1983-02-15 Robert Bosch Gmbh Fuel injection pump for internal combustion engine
US4408591A (en) * 1980-11-15 1983-10-11 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps
US5123393A (en) * 1991-09-04 1992-06-23 Stanadyne Automotive Corp. Timing control system for fuel injection pump
US5125802A (en) * 1989-12-19 1992-06-30 Zexel Corporation Injection timing control apparatus for distributor type fuel injection pumps
US5775306A (en) * 1994-07-15 1998-07-07 Lucas Industries Plc Advance mechanism
US20030056767A1 (en) * 2001-09-24 2003-03-27 Hopley Daniel J. Advance arrangement

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2839014A1 (de) * 1978-09-07 1980-03-20 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
GB2100030B (en) * 1981-05-28 1985-06-19 Lucas Ind Plc Fuel injection pumping apparatus
DE3532719A1 (de) * 1985-09-13 1987-03-26 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
GB8619994D0 (en) * 1986-08-16 1986-09-24 Lucas Ind Plc Fuel injection pump

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2961029A (en) * 1956-06-07 1960-11-22 Armstrong Cork Co Method of making resilient smoothsurfaced floor covering materials
US3051154A (en) * 1960-08-30 1962-08-28 Cav Ltd Liquid fuel pumps
US3331327A (en) * 1965-12-09 1967-07-18 Hartford Machine Screw Co Fuel pump
US3447520A (en) * 1966-06-06 1969-06-03 Cav Ltd Liquid fuel pumping apparatus
US3933159A (en) * 1971-02-09 1976-01-20 Molins Limited Manufacture of mouthpiece cigarettes

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1092727B (de) * 1957-04-25 1960-11-10 Cav Ltd Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2961029A (en) * 1956-06-07 1960-11-22 Armstrong Cork Co Method of making resilient smoothsurfaced floor covering materials
US3051154A (en) * 1960-08-30 1962-08-28 Cav Ltd Liquid fuel pumps
US3331327A (en) * 1965-12-09 1967-07-18 Hartford Machine Screw Co Fuel pump
US3447520A (en) * 1966-06-06 1969-06-03 Cav Ltd Liquid fuel pumping apparatus
US3933159A (en) * 1971-02-09 1976-01-20 Molins Limited Manufacture of mouthpiece cigarettes

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3869226A (en) * 1972-09-12 1975-03-04 Cav Ltd Fuel pumping apparatus
US3897764A (en) * 1973-05-18 1975-08-05 Cav Ltd Liquid fuel injection pumping apparatus
US3943902A (en) * 1973-07-13 1976-03-16 C. A. V. Limited Fuel injection pumping apparatus
US4074667A (en) * 1974-07-19 1978-02-21 C.A.V. Limited Liquid fuel injection pumping apparatus
US4050437A (en) * 1975-04-01 1977-09-27 Cav Limited Liquid fuel injection pumping apparatus
US4080109A (en) * 1975-07-05 1978-03-21 Lucas Industries Limited Fuel injection pumping apparatus
US4176640A (en) * 1976-04-20 1979-12-04 Lucas Industries, Limited Fuel injection pumping apparatus
US4365939A (en) * 1979-07-06 1982-12-28 Lucas Industries Limited Fuel injection pumping apparatus
US4366795A (en) * 1979-08-07 1983-01-04 Robert Bosch Gmbh Fuel injection pump for internal combustion engine
US4373492A (en) * 1979-08-07 1983-02-15 Robert Bosch Gmbh Fuel injection pump for internal combustion engine
US4408591A (en) * 1980-11-15 1983-10-11 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps
US5125802A (en) * 1989-12-19 1992-06-30 Zexel Corporation Injection timing control apparatus for distributor type fuel injection pumps
US5123393A (en) * 1991-09-04 1992-06-23 Stanadyne Automotive Corp. Timing control system for fuel injection pump
US5775306A (en) * 1994-07-15 1998-07-07 Lucas Industries Plc Advance mechanism
US20030056767A1 (en) * 2001-09-24 2003-03-27 Hopley Daniel J. Advance arrangement
EP1296052A3 (de) * 2001-09-24 2004-06-16 Delphi Technologies, Inc. Einrichtung zum Verstellen des Einspritzzeitpunktes
US6883499B2 (en) 2001-09-24 2005-04-26 Delphi Technologies, Inc. Advance arrangement

Also Published As

Publication number Publication date
FR1580052A (de) 1969-08-29
DE1776101B1 (de) 1972-01-13
GB1238283A (de) 1971-07-07

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