EP0049458A1 - Elektromagnetisch gesteuerte Kraftstoffeinspritzpumpe - Google Patents

Elektromagnetisch gesteuerte Kraftstoffeinspritzpumpe Download PDF

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Publication number
EP0049458A1
EP0049458A1 EP19810107712 EP81107712A EP0049458A1 EP 0049458 A1 EP0049458 A1 EP 0049458A1 EP 19810107712 EP19810107712 EP 19810107712 EP 81107712 A EP81107712 A EP 81107712A EP 0049458 A1 EP0049458 A1 EP 0049458A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel
plunger
pump
barrel
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.)
Granted
Application number
EP19810107712
Other languages
English (en)
French (fr)
Other versions
EP0049458B1 (de
Inventor
Aladar Otto Simko
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.)
Ford Werke GmbH
Ford France SA
Ford Motor Co Ltd
Ford Motor Co
Original Assignee
Ford Werke GmbH
Ford France SA
Ford Motor Co Ltd
Ford Motor Co
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 Ford Werke GmbH, Ford France SA, Ford Motor Co Ltd, Ford Motor Co filed Critical Ford Werke GmbH
Publication of EP0049458A1 publication Critical patent/EP0049458A1/de
Application granted granted Critical
Publication of EP0049458B1 publication Critical patent/EP0049458B1/de
Expired 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
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically

Definitions

  • This invention relates in general to a fuel injection pump for an internal combustion engine of the spark ignition type. More particularly, it relates to one that is compact, lightweight, economical to construct, and relatively simple in design.
  • the fuel pump of the invention is of the radial plunger, spill port type with an excess of fuel always delivered to the pumping chamber. Injection is consummated by controllably blocking a spill port to permit a buildup of pressure sufficient to open a conventional retraction type delivery valve and inject fuel through a fuel injection nozzle into the engine combustion chamber.
  • the present invention relates to an electromagnetically controlled pump of the radial plunger type utilizing a cam on a short engine driven camshaft, the cam being provided with acceleration and deceleration ramps to provide the desired characteristics to the pumping cycle.
  • the plunger barrel assembly serves three functions; namely, to house the pumping plunger at one end; to incorporate a fuel delivery valve at the opposite end without the necessity of a separate housing, and to provide a machined spill valve seat in the wall of the barrel at a location between the plunger and delivery valve.
  • the spill port is controlled by a valve that is universally seatable and self-aligning. It is actuated by an electromagnetic means, in this case a solenoid, that is constructed to assure a proper alignment of the valve in the barrel seat.
  • U.S. 3,880,131, Twaddel et al is another example of a radial plunger type pump with an electromagnetic means for controlling a spill port.
  • the plunger is not integrated with the delivery valve in the barrel of the pumping unit, nor is the electromagnetically operated valve of the self-aligning type for cooperation with a spill port in the barrel of the housing.
  • Hobo et al shows merely an on/off electromagnetically controlled valve to control the inlet supply of fuel to a pumping plunger.
  • the pump per se is not of the spill port type.
  • Omorie shows merely an on/off type electromagnetically controlled valve controlling the inlet supply of fuel to the pump as a function of a particular electrical signal from the engine.
  • Magata et al merely shows an electromagnetically controlled valve used in a fuel injection pump. It is not of the spill port type, nor is the plunger integrated with the delivery valve and a spill port. Eheim merely shows an on/off electromagnetically controlled valve controlling the inlet supply of fuel as a function of whether the engine is on or off. The fuel flow is controlled by a helix on a metering sleeve.
  • FIG. 4 in U.S. 1,957,435; Baur, shows the axial alignment of both the plunger and a delivery valve in the barrel of the pump.
  • This pump utilizes a helix type metering valve formed on the end of the plunger for control of the fuel flow and shows none of the advantages of this invention in the use of an electromagnetically operated spill port control valve as well as the other features enumerated above.
  • a primary object of the invention to provide a compact fuel injection pump of the spill port type having a radially extending plunger barrel assembly that contains a plunger and a delivery valve and a valve seat in the wall of the barrel that cooperates with a self-aligning spill port control valve operated selectively by an engine controlled electromagnetic means to selectively provide engine operation at the desired time as a function of various changing engine parameters.
  • Figure 1 illustrates a preferred embodiment of a fuel injection pump constructed according to the invention. It is essentially a two-piece assembly consisting of a one-piece aluminum housing 10 having at least one radial bore 12 within which is mounted a plunger barrel assembly 14.
  • the housing 10 has a central cavity 16 within which is received a short engine driven camshaft 18 that is rotatably mounted at opposite ends on a pair of ball bearing units 20 and 22.
  • Housing 10 supports bearing unit 20, while bearing unit 22 is supported within an annular cover plate 24 bolted to and closing the open side of housing 10, as shown.
  • a suitable oil seal 25 is provided, as shown.
  • Camshaft 18 in this case, is formed with a single cam 26 that is eccentrically mounted for reciprocation of a pumping plunger 30 engageable therewith.
  • the bottom of the plunger is flat and the plunger rides directly on the cam. While not shown, the cam profile would consist of an acceleration ramp, a constant velocity portion (Archimedes spiral) and a deceleration ramp.
  • the plunger 30 is slideably mounted in one end of a constant diameter bore 32 of a hardened steel plunger barrel 34.
  • the latter is fixedly mounted longitudinally within the housing bore 32 and keyed to housing 10 by an anti-rotation pin 36.
  • the fuel outlets to the engine fuel injectors are arranged at the other or upper end of bore 32.
  • the upper end 38 of the plunger barrel bore 32 also is formed as a housing for a fuel delivery valve 40 to seat thereagainst to block the flow of fuel to a fuel injection line 42.
  • the delivery valve is of the retraction type having a smaller flow cutoff land 44 at its lower end of a diameter that mates with the diameter of plunger bore 32, and a second larger diameter volume retraction land 46 at its upper end that can extend into the upper end of the plunger barrel for a short distance, as shown.
  • a spring 48 biases the delivery or retraction valve onto its seat in the barrel.
  • the preload of spring 48 is controlled by a nut 50 that is threadably adjustable into the upper end of housing 10 and provided with an annular seal 52 to prevent leakage of fuel out the housing.
  • the retraction valve operates in a known manner moving upwardly under the increased pressure of the fuel as pumping plunger 30 moves upwardly through a pumping stroke.
  • the pressure of the fuel in injection line 42 will decrease to a point where the spring 48 will be able to move the retraction valve 40 downwardly into the bore 32.
  • the first effect is for the end of land 44 to engage the bore and shut off the communication of fuel between bore 32 and the fuel injection line 42.
  • the second effect upon continued movement of the valve is to decrease the residual pressure in the fuel injection line 42 by the mass of the retraction valve moving downwardly into the upper part of the plunger bore, which increases the effective volume in the spring chamber.
  • Housing 10 is formed with a fuel annulus 54 around the upper end of the stationary plunger barrel 34. This annulus is connected to a source of low pressure fuel through a feed passage 58 intersecting an annular fuel passage 60 in turn connected to a fuel inlet supply line 62. A sleeve 63 seals the passages from leakage into cavity 16. A low pressure supply pump, not shown, would be included in the system to maintain the fuel in inlet 62 at a low pressure. Fuel leaking past plunger 30 is vented through plunger barrel bores 62, an annulus 64, a line 66 connected to a second annulus 68, and a drain or vent line 70.
  • the pressurization of fuel by plunger 30 is controlled by an inlet-spill port type construction. That is, a through port 72 connects the fuel feed or supply line 58 to the fuel chamber 74 defined in bore 32 between the upper end of plunger 30 and the lower end of delivery 44. So long as spill port 72 remains open, upward movement of plunger 30 will merely move the fuel in chamber 74 out through the spill port 72 and back into the feed line 58. When the spill port 72 is closed, the upward movement of plunger 30 can then pressurize the fuel sufficient to open the delivery valve 40 for flow of fuel to and through the injection line 42.
  • the spill port 72 in this case is controlled by an electromagnetically controlled ball valve 75.
  • the radially outer edge of spill port 72 is formed as a seat for the ball valve 75, which is universally seatable.
  • Housing 10 is provided with a multi-diameter recess 76 in which is slideably and tiltably mounted a valve actuator 78.
  • the latter consists of a stem portion 80 fixedly attached to the ball valve and formed with a mushroom shaped head portion 82.
  • the latter has a spherical surface 84 that constitutes a radius of curvature from the center line of the ball 75.
  • the actuator in this case is biased by a spring 87 against the movable armature 88 of a solenoid 90 mounted in a recess 92 in housing 10.
  • the solenoid is located in place by an annular retainer 94 and a biasing spring member 96. Since any point on surface 84 is a point on a radius from the centerline of the spill port when the ball valve is seated, any slight misalignment of the centerline of the solenoid armature 88 with respect to the center line of the spill port 72 will merely result in a tangential point contact between some point on the end of the armature and the spherical surface 84 so that forces still are transmitted along the radius and side forces are eliminated. Therefore, the force exerted by the armature will always act through the center of the ball on the spill hole.
  • camshaft 18 in this case is adapted to be driven by an internal combustion engine, through a pulley 100 secured to the camshaft.
  • a gear could be substituted for the pulley, if desired.
  • cam and one plunger barrel assembly is indicated, it will be clear that any multiple of the same could be incorporated into the design without departing from the scope of the invention.
  • the pump design lends itself well for 4, 6 and 8 plunger arrangements because identical pumping elements and camshaft can be used while only the housing changes.
  • Figures 2-5 show an alternative construction of the spill port valve control. This construction differs from that shown in Figure 1 with respect to the valve element and the means for retaining the ball valve 75 in position.
  • the ball is the total valve element.
  • a cylindrically shaped spring 102 of thin gauge stock surrounds the pump plunger barrel 34 and is contained within a reduced diameter recess 104 in the barrel body. One end of the spring is punched out to form prong-like ends 106 to engage the ball valve 74 and retain it in position, normally biasing it away from the seat of the spill port 72.
  • the opposite side of spring 102 is provided with a pair of tangs 108 that fit within a slot 110 in a cylindrical retainer spring 112. The latter also is formed of thin gauge stock to surround the plunger barrel.
  • the upper end of the retaining spring 112 is formed with a tab 114 positionable in a small recess 116 in plunger barrel 34 for circumferentially and axially locating the spring. In this case, until the solenoid is energized, the spring ends 106 will maintain the ball valve away from the seat of the spill port 72 and thus prevent pressurization of the fuel passage 42.
  • the engine driven camshaft 18 will rotate and force the plunger 30 upwardly through a pumping stroke.
  • an engine control such as a microprocessor unit, for example, will cause energization of solenoid 90 causing a leftward axial movement of the armature 88 and a similar movement of the plunger 78 and the ball valve 75.
  • This movement which is about . 0 , 07mm for example, will seat the ball valve in the spill port 72 against the force of spring 87.
  • the injection line is adapted to be connected to a conventional fuel injector of the pressure relief type, which above a predetermined fuel pressure opens to inject fuel into the engine proper. In this case, therefore, pressurization of fuel chamber 74 to a level sufficient to open the fuel injector will effect passage of fuel out through passage 42.
  • solenoid 90 When the engine control decides that the volume of fuel injected is sufficient for the particular load demand or other condition required, solenoid 90 will then be deenergized. This will immediately permit the pressure of fuel in chamber 74 acting against the ball valve 74 and the force of spring 87 to move the ball valve rightwardly as seen in Figure 1 away from the spill port seat. This will cause a decay of pressure in chamber 74 by passage of fuel into the feed line 58. Accordingly, the pressure of fuel in line 42 will decay until a level is reached at which the force of spring 48 is sufficient to overcome the pressure of fuel on the delivery valve 40. This will allow the lower end of the valve to enter into the upper end of the plunger barrel bore 32 to shut off communication between the injection line 42 and the supply chamber 74.
  • the above cycle is repeated when the pump plunger again moves on its pumping stroke, if the solenoid is again energized.
  • the duration of injection and the quantity of fuel injected will be determined by the length of time the solenoid 90 is energized to close spill port 72. This will be determined in accordance with design parameters and operating conditions of the engine, in a desired manner.
  • the invention provides a plunger type fuel injection pump of a simple construction having essentially a one-piece housing enclosing a plunger barrel assembly that incorporates a plunger and a delivery valve and a spill port all within a common diameter bore, thus providing an economical construction, and coupled with a self-aligning spill port control valve that permits slight misalignment of the valve actuator without causing side forces to act on the valve.

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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)
EP19810107712 1980-10-06 1981-09-29 Elektromagnetisch gesteuerte Kraftstoffeinspritzpumpe Expired EP0049458B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US19398580A 1980-10-06 1980-10-06
US193985 1980-10-06

Publications (2)

Publication Number Publication Date
EP0049458A1 true EP0049458A1 (de) 1982-04-14
EP0049458B1 EP0049458B1 (de) 1985-04-17

Family

ID=22715863

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19810107712 Expired EP0049458B1 (de) 1980-10-06 1981-09-29 Elektromagnetisch gesteuerte Kraftstoffeinspritzpumpe

Country Status (4)

Country Link
EP (1) EP0049458B1 (de)
JP (1) JPS5791371A (de)
CA (1) CA1182356A (de)
DE (1) DE3170004D1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2119031A (en) * 1982-04-19 1983-11-09 Toyota Motor Co Ltd Fuel injection device for internal combustion engine
DE3501249A1 (de) * 1984-01-21 1985-07-25 Lucas Industries P.L.C., Birmingham, West Midlands Fluessigkraftstoff - einspritzpumpvorrichtung
FR2568317A1 (fr) * 1984-07-27 1986-01-31 Hatz Motoren Dispositif d'injection de combustible
GB2276677A (en) * 1993-03-30 1994-10-05 Lucas Ind Plc Fuel injection pump
GB2292423A (en) * 1994-08-17 1996-02-21 Lucas Ind Plc Pump for fuel injection

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1664608A (en) * 1924-05-12 1928-04-03 Louis O French Fuel-injection system
DE2018112A1 (de) * 1969-05-19 1970-12-03
FR2107690A5 (de) * 1970-09-18 1972-05-05 Bosch
FR2299523A1 (fr) * 1975-01-28 1976-08-27 Bosch Gmbh Robert Pompe d'injection de carburant pour moteur a combustion interne
GB2013275A (en) * 1978-01-31 1979-08-08 Lucas Industries Ltd Liquid fuel pumping apparatus
GB2051970A (en) * 1979-06-25 1981-01-21 Gen Motors Corp Solenoid valve controlled fuel injection pump

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3779225A (en) * 1972-06-08 1973-12-18 Bendix Corp Reciprocating plunger type fuel injection pump having electromagnetically operated control port
US3880131A (en) * 1973-06-28 1975-04-29 Bendix Corp Fuel injection system for an internal combustion engine
JPS587842Y2 (ja) * 1978-06-30 1983-02-12 ナショナル住宅産業株式会社 ベランダ用水切装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1664608A (en) * 1924-05-12 1928-04-03 Louis O French Fuel-injection system
DE2018112A1 (de) * 1969-05-19 1970-12-03
FR2107690A5 (de) * 1970-09-18 1972-05-05 Bosch
FR2299523A1 (fr) * 1975-01-28 1976-08-27 Bosch Gmbh Robert Pompe d'injection de carburant pour moteur a combustion interne
GB2013275A (en) * 1978-01-31 1979-08-08 Lucas Industries Ltd Liquid fuel pumping apparatus
GB2051970A (en) * 1979-06-25 1981-01-21 Gen Motors Corp Solenoid valve controlled fuel injection pump

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2119031A (en) * 1982-04-19 1983-11-09 Toyota Motor Co Ltd Fuel injection device for internal combustion engine
DE3501249A1 (de) * 1984-01-21 1985-07-25 Lucas Industries P.L.C., Birmingham, West Midlands Fluessigkraftstoff - einspritzpumpvorrichtung
FR2568317A1 (fr) * 1984-07-27 1986-01-31 Hatz Motoren Dispositif d'injection de combustible
GB2276677A (en) * 1993-03-30 1994-10-05 Lucas Ind Plc Fuel injection pump
GB2276677B (en) * 1993-03-30 1995-09-06 Lucas Ind Plc Fuel pump
US5517973A (en) * 1993-03-30 1996-05-21 Lucas Industries Public Limited Company Fuel pump
GB2292423A (en) * 1994-08-17 1996-02-21 Lucas Ind Plc Pump for fuel injection

Also Published As

Publication number Publication date
CA1182356A (en) 1985-02-12
JPS5791371A (en) 1982-06-07
EP0049458B1 (de) 1985-04-17
DE3170004D1 (en) 1985-05-23

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