Search Images Maps Play YouTube News Gmail Drive More »
Sign in
Screen reader users: click this link for accessible mode. Accessible mode has the same essential features but works better with your reader.


  1. Advanced Patent Search
Publication numberUS3115304 A
Publication typeGrant
Publication dateDec 24, 1963
Filing dateOct 11, 1961
Priority dateOct 11, 1961
Publication numberUS 3115304 A, US 3115304A, US-A-3115304, US3115304 A, US3115304A
InventorsHarvey G Humphries
Original AssigneeGen Motors Corp
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Fuel injector pump with hydraulically controlled injection valve
US 3115304 A
Abstract  available in
Previous page
Next page
Claims  available in
Description  (OCR text may contain errors)

Dec`. 24, 1963 H. G. HuMPHRn-:s 3,115,304



ATTORNEY v United States Patent O 3,115,304 FUEL INJECTOR PUMP WiTH HYDRAULICALLY CONTROLLED INJECTION VALVE Harvey G. Humphries, Birmingham, Mich., assigner t General Motors Corporation, Detroit, Mich., a corporation of Delaware Filed ct. 11, 1961, Ser. No. 144,492 6 Claims. (Cl. 239-90) This invention relates to fuel injection apparatus, an-d particularly `to unit type -fuel injector-pumps for diesel engines.

In such unit injector-pumps employing a reciprocating plunger type pump it has long been known that a needle type valve, openable upon build-up of sufficient fuel pressure in the pumping cylinder, provides a very sharp and positive fuel cut-olf at the end of injection. However, I have found that with only minor modification of the conventional |injector of this type, these advanta-ges can be further enhanced by subjecting the needle Valve at the proper time to injection p-ressure to assist its closing action.

As the preferred arrangement for carrying out this objective, I provide the unit with an additional passage which connects the needle -valve spring chamber with a side port in the pumping cylinder, which port is closed by the plunger during substantially the entire injection period but is uncovered by the plunger at or slightly prior to the end thereof. Also, in accordance with my invention, since such ending of injection is effected (as is con- Ventional) by the plunger uncovering another port which Vents the pumping cylinder of fuel pressure developed by the advancing plunger, I restrict the rate at which such venting may occur. As a result, the needle valve closing action effected by the injection pressure in the pumping cylinder is assured, and the further advantage is obtained of employing at least some of this pressure to assist return lof the pump plunger by its spring and thereby maintain Contact between the plunger driving cam and the plunger or its cam follower. Thus a more precise timing of -fuel injection, together with quieter operation of the unit injector-pump, is accomplished.

As a further feature of the invention, I provide the tip passage, through which the fuel is delivered from the pumping cylinder to open the needle valve and discharge into the engine, with an anti-blow-back or check valve arranged to accommodate restricted leakage in its closed position. Thereby, such fuel as may be trapped between this check valve and the needle Valve, when both are closed, is permitted to dissipate gradually. This insures against the needle valve being forced open, with resultant after-dribble of fuel, following the initial closing of the needle valve, yet does not affect the main function of the check valve -in preventing blow-back of engine combustion gases into the pumping cylinder in the event the needle valve should happen to stick open.

A better understan-ding of the manner in which these and other objects and advantages of the invention are realized will be apparent from the following description of one specific embodiment thereof selected for illustration, having reference to the drawings, wherein:

yFIGUR-E l is a longitudinal sectional View through a unit injector-pump showing the arrangement for employing injection pressure to assist closing of the needle valve, together with the improved check valve and ineans for delaying dissipation of injection pressure in the pumping cylinder at the end of the injection stroke. In this view, the parts are shown in their relative positions at the beginning of the downward or injection stroke of the plunger.

IFIGURE 2 is a fragmentary View similar to FIGURE 3,115,304 Patented Dec. 24, 1963 2 1, but showing the parts in the-ir positions during full injection.

FIGURE 3 is a similar 'fragmentary View, showing the parts in their positions at the end of injection.

FIGURE 4 is a transverse sectional view taken substantially along the line 4 4 of FIGURE 1.

FIGURE 5 is Ian enlarged sectional view taken substantially along the line 5-5 of FIGURE 4, illustrating details of the construction and arrangement of the check valve.

Referring now to the drawings in detail, and first to FIGURE l, the upper porti-on of the unit is conventional and comprises a housing 1 in which is lixedly supported a bush-ing 2. Reciprocable therein is a plunger 3 whose upper end is connected to a cam follower 4, and between this follower and the housing is a plunger return spring 5 urging the plunger outwardly of the bushing. The bore 6 of the bushing below the plunger 3 constitutes the pumping cylinder, and surrounding the bushing is an annular reservoir 7 into which fuel may be introduced (via passages 3, 9, 10 and filter 11) from an external fuel connection 12. This reservo-ir is contained in a lower housing or nut 13 whose upper end is threadedly connected as 4at i4 to the housing l. Adjacent its lower end, the plunger 3 has the usual bypass means in the form of an external metering :groove 16 and transverse and axial passages 119 and 20, by which upper and lower inlet and bypass ports 17 and 1S are connectable with lthe pumping cylinder 6 during the downward or pumping stroke of the plunger. The sides ports 17 and 18, as will be seen, are in communication with the reservoir chamber 7 so that when the plunger is in its uppermost position shown the pumping cylinder and all passages and ports connected with it are filled with fuel. The lower end of the cylinder is open for fuel displaced by the plunger during its downward stroke, such fuel being delivered via a passage 2d, and connecting passages 22 and 23, to an annular passage 24 surrounding a needle type injection valve 25 and terminating with an outlet in the form of spray orifices 2.6 in the lower end of the spray tip y27'. Passages 2li-24 are referred to as the fuel delivery passage, or tip passage.

The needle valve Z5, whose lower end normally closes off fuel flow through the outlet 26 by engaging the conical seat 28 at the spray tip, is slidably guided adjacent its upper end in a spacer block 29. A bore 36 is provided in the latter for this purpose and opens at its upper end into a spring chamber 3l. in the construction shown, this spring chamber is partly formed in the lower spacer block 29, and partly in an intermediate spacer block 32. The upper end of the spring chamber is closed by an upper spacer block 33 which abuts the lower end of the bushing 2. It Will be noted that the needle Valve 25 is movable into the spring chamber 31 in its opening direction, against a coil spring 34 tending to bias the valve closed, this spring being seated at its upper end against the upper spacer block 33 and at its lower end on a spring seat 35 carried by the upper end of the needle valve. This spring seat extends upwardly within the spring chamber a sufficient distance to limit opening travel of the needle valve by abutment with the upper spacer block 33 (FIGURE 2).

Opposite the lower inlet and bypass port 1-8 there is provided an additional port 36 which is connected via passages 37, 38 and 39 Iwith the spring chamber 31 at all times. Being located at or at substantially the same height in the pump cylinder as the lower inlet and bypass port 18, this port 36 remains covered by the plunger 3 during its pumping stroke (FIGURE 2) until the metering groove 16 on the plunger uncovers it at substantially the same time the port i8 is uncovered by the plunger (FIGURE 3). Such uncovering of the spring cage port 36 preferably occurs slightly in advance, eg. .005-.0115 inch of plunger travel, of the uncovering of the port 18 by the groove 16.

Check valve means is provided between the pumping cylinder and the injection valve to prevent blow-back of combustion gases through the orifices 2.6 and tip passage 21-24 to the pumping cylinder in the event the needle valve should fail to close during operation. In the arrangement shown, this check valve means takes the form of the flat wafer 40 located in a counterbore 41 provided at the upper end of the passage 22 in the intermediate spacer block 32. In its normal position shown this check valve lies against the bottom of the counterbore 41, and -fuel is free to iiow past the check valve via a slot 42 milled transversely through the counterbore as best shown in FIGURES 4 and 5. 'in the event of combustion gas blow-back, the flat `disc moves into abutment with its seat 43 on the lower -face of the upper spacer block 33, substantially blocking reverse fluid flow into lthe pump cylinder via the passage 21. A restricted leakage path for some iiow past the closed check vaive when thus seated is provided, however, by a small central orifice 44 in the disc 40.

lDuring operation, downward movement of the plunger on its pumping stroke initially closes off ports 18 and 36, following which continued downward movement of the plunger results in fuel within the pumping cylinder being bypassed through the plunger passages 2f) and 19 to the groove 16 and back to the lfuel supply reservoir 7 via the upper inlet and bypass port y17. When the plunger has moved down far enough to also close the latter port 17 fuel pressure quickly builds up in the cylinder 6 and tip passage 21-24 sufficiently to raise the needle valve off its seat 2S and begin injection through the outlet orifices 26. The `fuel pressure within the spring chamber 31 at this time is relatively low (substantially the same as that in fuel supply reservoir 7) and does not prevent the needle valve lfrom moving upwardly in its opening direction. Upon the plunger movingdownwardly a sufficient distance (FIGURE 3) that the groove 16 uncovers the spring chamber port 36, the relatively high `fuel injection pressure within the pump cylinder 6 is transmitted to the spring chamber 31 where it acts therein to supplement the needle valve spring 34- in effecting quick closing of `the needle valve. Simultaneously, or immediately thereafter, the plunger groove 16 also uncovers the lower fuel inlet and bypass port 1S, venting the pump cylinder to the fuel supply' reservoir 7, `with the result that fuel pressure in the tip passage 21-24 falls off sharply to allow the needle valve to close. Any relatively higher pressure of the fuel below the check Valve than above it in the -tip passage 2li-24, as might cause the check valve to close after the needle valve 25 has closed, will be bled off gradually through the restricted orifice 43 in the check valve disc. Such bleed-off precludes fuel trapped between the check valve and needle valve from interfering with closure of the needle valve, or 'from reopening the needle valve, which would result in after-dribble of fuel beyond the normal ending Yof injection.

Preferably the lower inlet and bypass port 18 is made suiiiciently small to restrict its flow capacity such that dissipation of the injection fuel pressure in the pump cylinder is delayed upon the plunger groove 16 uncovering this port to terminate injection (FIGURE 3). As a result fuel pressure in the pump cylinder at the end of the injection yieldingly opposes further downward movement of the plunger. Were it not for this feature, too rapid a decrease in fuel pressure opposing such downward movement of the plunger could result in initiating a surging action in the plunger return spring 5, and its possibility of breakage. The extent of the restriction of the size of port 1S must, of course, be selected in accordance with the pumping displacement, operating speed and plunger return spring loading in the particular fuel injector unit to be used, but in general it is desirable that the restriction be such as to maintain sufficient pressure in the pump chamber to minimize the increase in the downward velocity of the pump plunger at the uncovering of port 18.

While only a single preferred embodiment of the invention has been disclosed, it is appreciated that numerous minor changes in the construction and arrangement of the parts may be made without departing from the spirit and scope of the invention as defined in the following claims.

I claim:

rl. In a unit fuel injector-pump, a relatively low pressure fuel supply connection, a pumping cylinder, a pump plunger reciprocable in the cylinder, said cylinder having two side ports each sequentially closable and openable by the plunger during its pumping stroke and an opening for fuel displaceable by the plunger during the portion of said stroke when both said ports are closed, a fuel delivery passage connected to said opening and terminating with an outlet, an injection value normally closing said outlet but movable to open the same in response to a predetermined relatively high fuel pressure developed in the cylinder by the plunger during said portion of its pumping stroke, a chamber separate from said passage, said valve being exposed to pressure in said chamber acting thereon in the direction toward closure of said outlet, said plunger having bypass means connected to said opening and connectable to said ports in response to opening of said ports by the plunger, one of said ports being connected to said supply connection for venting said relatively high fuel pressure developed in the cylinder to the supply connection in response to connecting said bypass means to said one port, `the other of said ports being connected to said chamber Ifor applying said relatively high fuel pressure thereto from the cylinder to bias the valve closed in advance of said venting of the cylinder to the supply connection, said chamber being in direct iiuid communication solely with said other port.

2. The invention of claim 1, wherein opening movernent of said injection valve is in the direction toward said chamber, and a spring is provided in said chamber and acts on the valve to bias it closed.

3. The invention of claim 2, together with check valve means in said passage between said opening and injection valve, said check valve means being closable toward said opening.

4. The invention of claim 3, wherein said check valve ,means includes a check valve, a seat therefor, and means References -Cited in the file of this patent UNITED STATES PATENTS 2,951,643 Engel Sept. 6, 1960 FOREIGN PATENTS 483,468 Italy July 30, 1953

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US2951643 *Mar 13, 1958Sep 6, 1960Gen Motors CorpFuel injector with pilot injection
IT483468B * Title not available
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3364863 *May 31, 1966Jan 23, 1968Jerzy D. OlszewskiFuel injection system
US3368491 *Jun 22, 1966Feb 13, 1968Murphy Diesel CompanyFuel injection pump
US3403632 *Mar 3, 1967Oct 1, 1968Gen Motors CorpExternal spring needle valve fuel injector
US3450351 *Oct 18, 1966Jun 17, 1969Bosch Gmbh RobertFuel injection nozzle for internal combustion engines
US3465677 *Oct 4, 1967Sep 9, 1969Cav LtdLiquid fuel pumping apparatus
US3482519 *Mar 13, 1968Dec 9, 1969Cav LtdLiquid fuel pumping apparatus
US3486696 *Dec 4, 1967Dec 30, 1969Allis Chalmers Mfg CoFuel injector
US3593924 *Feb 11, 1970Jul 20, 1971Bosch Gmbh RobertValve for the advance and main injection of fuel
US3628895 *Nov 4, 1969Dec 21, 1971Lucas Industries LtdLiquid fuel pumping apparatus
US3640466 *Oct 24, 1969Feb 8, 1972Sulzer AgFuel injection system for an internal combustion piston engine
US3738576 *Apr 21, 1971Jun 12, 1973Physics Int CoInjection nozzle for direct injection engine
US3747857 *Jun 24, 1971Jul 24, 1973Cav LtdFuel injection systems
US3980234 *Jun 13, 1975Sep 14, 1976Stanadyne, Inc.Fuel injection nozzle
US4065058 *May 21, 1976Dec 27, 1977General Motors CorporationFuel injection nozzle with compressible valve
US4579283 *Jun 11, 1984Apr 1, 1986Nippon Soken, Inc.Pressure responsive fuel injector actuated by pump
US4750462 *Jun 11, 1986Jun 14, 1988Robert Bosch GmbhFuel injection apparatus for internal combustion engines
US4979676 *Oct 20, 1989Dec 25, 1990Robert Bosch GmbhFuel injection device for internal combustion engines
US5419492 *Mar 10, 1994May 30, 1995Cummins Engine Company, Inc.Force balanced electronically controlled fuel injector
US5553781 *Jan 3, 1995Sep 10, 1996Servojet Products InternationalConversion of jerk type injector to accumulator type injector
US5743237 *Jan 28, 1997Apr 28, 1998Caterpillar Inc.Hydraulically-actuated fuel injector with needle valve operated spill passage
US5769319 *Mar 14, 1997Jun 23, 1998Cummins Engine Company, Inc.Injection rate shaping nozzle assembly for a fuel injector
US5823429 *Jul 12, 1996Oct 20, 1998Servojet Products InternationalHybrid hydraulic electronic unit injector
US5826802 *Nov 17, 1995Oct 27, 1998Caterpillar Inc.Damped check valve for fluid injector system
US5865373 *Jan 9, 1997Feb 2, 1999Lucas IndustriesFuel Pump/injector
US5870996 *Apr 10, 1998Feb 16, 1999Alfred J. BuescherHigh-pressure dual-feed-rate injector pump with auxiliary spill port
US6009850 *Apr 10, 1998Jan 4, 2000Alfred J. BuescherHigh-pressure dual-feed-rate injector pump with grooved port-closing edge
US6655603 *Apr 18, 2002Dec 2, 2003Caterpillar IncReverse flow valve for fuel injectors
US6793159Jun 18, 2003Sep 21, 2004Seimens AktiengesellschaftFuel injector
US7510127Feb 4, 2004Mar 31, 2009Caterpillar Inc.Variable flow rate valve and method of reducing wear on same
US7891587 *Oct 9, 2006Feb 22, 2011Robert Bosch GmbhIntermediate plate for a fuel injector, and fuel injector
US20050167523 *Feb 4, 2004Aug 4, 2005Goudarz HajiVariable flow rate valve and method of reducing wear on same
US20080237373 *Oct 9, 2006Oct 2, 2008Patrick MattesIntermediate Plate for a Fuel Injector, and Fuel Injector
DE2558790A1 *Dec 24, 1975Jul 14, 1977Bosch Gmbh RobertKraftstoffeinspritzduese fuer brennkraftmaschinen
DE2602280A1 *Jan 22, 1976Jul 29, 1976Diesel Kiki CoHochdruck-kraftstoffeinspritzeinrichtung fuer dieselmotoren
EP0091862A1 *Apr 5, 1983Oct 19, 1983The Bendix CorporationDouble dump single solenoid unit injector
EP0204982A2 *May 13, 1986Dec 17, 1986Robert Bosch GmbhFuel injection for internal-combustion engines
EP0204982A3 *May 13, 1986Feb 22, 1989Robert Bosch GmbhFuel injection for internal-combustion engines
EP1026393A2 *Feb 1, 2000Aug 9, 2000Siemens AktiengesellschaftInjector for the injection system of an internal combustion engine
WO1996021102A1 *Dec 29, 1995Jul 11, 1996Servojet Products InternationalConversion of jerk type injector to accumulator type injector
WO2002050422A1 *Dec 12, 2001Jun 27, 2002Siemens AktiengesellschaftFuel injector
U.S. Classification239/90, 417/494, 239/584, 239/93, 239/533.8
International ClassificationF02M57/02
Cooperative ClassificationF02M2700/078, F02M57/02
European ClassificationF02M57/02