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.

Patents

  1. Advanced Patent Search
Publication numberUS2173814 A
Publication typeGrant
Publication dateSep 19, 1939
Filing dateMay 10, 1939
Priority dateMar 15, 1938
Publication numberUS 2173814 A, US 2173814A, US-A-2173814, US2173814 A, US2173814A
InventorsBischof Bernhard
Original AssigneeBischof Bernhard
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Fuel injection apparatus for internal combustion engines
US 2173814 A
Images(3)
Previous page
Next page
Description  (OCR text may contain errors)

B. BISCHOF Sept. 19, 1939.

FUEL INJECTION APPARATUS FOR INTERNAL COMBUSTION ENGINES 3 Sheets-Sheet 1 Filed May 10, 1939' whom Lew Sept. 19, .1939.

FUEL INJECTION APPARATUS FOR INTERNAL comausnon ENGINES Filed May 10, 1959 iii BISCHOF 3 Sheets-Sheet 2 CIHO mew Sept. 19, 1939. B. BISCHOF 2,173,814

FUEL INJECTION APPARATUS FOR INTERNAL COMBUSTION ENGINES Filed May 10, 1939 3 Sheets-Sheet 3 61a 91 89 82a 62a 65a 9 g as a? z 1; as .2. 49a

as 72a 92 48a 1 63a 58; k 43 l I lumen/row UZDQWm/Lb ZED Adm F who/aw ys Patented Sept. 19, 1939 UNITED STATES FUEL INJECTION APPARATUS FOR, INTER- NAL COMBUSTION ENGINES Bernhard Bischof, Winterthur, Switzerland Application May 10, 1939, Serial No. 272,916 In Switzerland March 15, 1938 12 Claims.

This invention relates to fuel injection devices for internal combustion engines and particularly for Diesel engines.

The invention provides for preliminary injection of a small quantity of fuel, followed after a short interval by the main injection. This twostage injection is effected by the use of a novel fuel injection valve in conjunction with a fuel feeding pump of the known spill-back charge measuring type, modified only in, such a way as to ensure a definitely limited reflux of fuel at the end of its delivery period.

The fuel injection valve is of the type in which a needle valve loaded in a closing direction is forced open by the delivery to its inlet side of fluid under pressure suflicient to overcome the loading. The delivery connection of the pump is normally not connected directly to the injection valve, but leads to a cylinder in which a preliminary injection piston has limited motion. The space beyond this piston is in communication with the injection valve and such space is' charged with fuel at the end of each cycle, so

that when the pump initially delivers fuel, the delivered fuel shifts the preliminary injection piston a definite amount. This piston forces fuel trapped beyond it into the injection valve, causing the valve to open and effect preliminary injection, fixed in amount, and then close.

The preliminary injection piston has certain valve functions and when displaced as just described, admits fuel under pressure against a loading piston. The resulting shift of the loading piston increases the loading of the injection valve assuring that it is held closed after its opening and closing to effect preliminary injection.

The loading piston is also a valve, and its loading shift completes a connection partially established by the preceding shift of the preliminary injection piston. The'connection so completed is from the delivery connectionof the pump directly to the fuel injection valve, so thatwhen the pump develops pressure suincient 5 to overcome the augmented loading of the injection valve, this valve opens and the principal injection occurs.

When the pump ends delivery and a slight reflux of fuel occurs, the injection valve closes sharply, the preliminary injection and loading pistons are restored, and during their restoration deliver fuel to charge the space between the preliminary injection piston and the injection valve, thus conditioning the parts for the next cycle. The above general statement of the principle of operation is made to facilitate understanding of the following detailed description of two practical embodiments of the invention, shown in the accompanying drawings.

In the drawings:

Figure 1 is a view partly diagrammatic, showing ameasuring fuel pump connected to deliver fuel to a fuel injection valve which is mounted in the cylinder head of an internal combustion engine. The pump and injection valve are shown in axial section and in the positions assumed at the start of the injection cycle.

Figure 2 is an enlarged view of a portion of the injection mechanism in the position of Figure 1.

Figure 3 is a view similar to Figure 2, but showing the parts in the positions assumed during the main injection.

Figure 4 is a view of a modified injection valve with the parts in the positions characteristic of Figures 1 and 2.

Refer first to Figures 1-3 inclusive.

In Figure 'l, the fuel pump is indicated generally at A and the fuel injection valve at B.

The shaft 6 is driven by the engine shaft and makes one turn for each combustion cycle of the engine. It carries a cam I which reacts against a cup-shaped cross head 8 guided in the housing 9.

Mounted on housing 9 is a cylinder I I having a working space I2 in which a piston I3 works. The piston has a stem It in thrust relation with cross head 8 and is urged downward by the coil compression spring I5. Swiveled on the lower end of cylinder II is a pinion I6, which is splined at I! to stem M. A rack I8 meshes with pinion I6 and may be actuated manually or by automatic means such as a governor (not shown) to adjust the piston I3 angularly without restraining its reciprocation. Angular adjustment of the piston varies the effective working stroke of the pump piston by controlling a spill-back to the pump intake.

The pump intake port is shown at I9 and is exposed by the upper end of piston I3 when the latter is at its lowermost position (Figure 1) A groove 2I encircles the piston in position to register with port I9 when the piston is in its uppermost position. To this groove 2I a slot 22 leads from the end of the piston, the slot having one side of spiral form as indicated at 23. This side 23 forms a control edge to coact with port I9 and time the spill-back according to the angular position of the piston I3. A fuel supply indicated as a tank 24 delivers fuel under moderate head through tube 25 to port I9. I

The mechanism so far described is simply a well known spill-back measuring pump.

The discharge fitting 26 retained by sleeve nut 21 houses a discharge valve of special form. Thedischarge port 28 leads from working space l2 and has a valve seat 29 at its upper end. A poppet valve 3| with fluted, pilot 32 coacts with seat 29 toward which it is urged by coil compression spring 33. The lift of the valve is limited by stop 34 and is such that a piston-like flange 35 carried by pilot 32 and fitting freely in port 28 rises above seat 29 as the valve approaches fully open position.

The space 36 beyond valve 3| is connected through ports 31 with pump discharge tube 38 which leads to the body of the fuel injection valve.

When piston I3 starts its upward stroke it first blanks port l9. Discharge through port 28 then commences, and since piston 35 on valve 3| displaces liquid ahead of it, displacement into tube 38 starts at once When control edge 23 overtravels port l9, displacement stops because port I9 is open and back flow can occur. A definite reflux from tube 33 to working space I2 occurs and is measured partly by the unavoidable slip through the valve as it closes and partly by the displacement of piston 35 after it enters port 28.

Thus the total quantity of fuel discharged (and the duration of discharge) are varied by the angular adjustment of the piston, but the amount of reflux in tube 38 is virtually fixed and uniform, and occurs after each delivery stroke. This reflux has functional significance with respect to the operation of the injection valve, now to be described. L

In Figure 1 a portion of the cylinder head of an internal combustion engine appears at 4| and 42 is a. portion of the working space into which fuel is to be injected. The head 4| has a bore- 43 to receive the shell 44 of the injection valve, which shell seats on a shoulder 45 as shown. The means for retaining the shell against cylinder pressure are not shown but would be conventional.

For convenience in manufacture, the body mounted in shell 44 is made in four parts which abut on plane surfaces and are held in sealing engagement by the annular head 46 screwed into the end of shell 44. These four parts are the nozzle member 41 which projects into the working space 42, the loading spring housing 48, the cylinder member 49 and the inlet cap 5|, to which last the tube 38 is connected.

Leading through the tip of nozzle member 41 from fuel chamber 52 to working space 42 are the injection ports 53. These are controlled and normally closed by injection valve 54 connected by a slender stem 55 to a larger plunger 56. The plunger is urged in a valve opening direction by fluid pressure in chamber 52, because its lower end is exposed to fluid in said chamber.

The plunger 56 makes a fluid tight sliding fit in an axial bore in member 41 and its upward motion and consequently the lift of valve 54 are limited by collision of the plunger with the lower face of member 48 (see Figure 3) The member 48 has a smaller aligned bore through which a stem 51 carried by and smaller than plunger 56 passes, entering a large spring chamber 58 within which it carries a disc shaped spring seat 59.

Extending part way-through member 49 and terminating in a chamber 6| is a cylinder bore displacing sition (Figure 1).

which receives the loading piston 62 which makes a fluid tight sliding fit therein. The piston 62 should be as large as or larger than the plunger 56 against whose action it must load, by means of a hydrostatic pressure which at times is no higher than that acting on plunger 56.

Piston 62 carries at its lower end a disclike spring seat 63 between which and seat 59 a coil compression loading spring 64 is confined. The spring seat 63 also serves to limit downward motion of piston 62 by engaging stop shoulder 65 in chamber 58. In this way the augmented loading is positively limited.

A check valve 66 permits flow-from chamber 6| to supply chamber 61 with which tube 38 is in free communication by way of passage 68. Valve 66 is spring loaded in a closing direction as shown, and carries a flange 69 which retards and does not inhibit flow past the valve. It offers a convenient way to limit flow through a valve of substantial size.

A fuel supply passage 1| leadsthrough members 41 and 48 to chamber 52 around the injection valve. An eccentrically located cylinder 12 formed in member 49 is interposed between supply chamber 61 and passage 1|, but direct communication by way of such cylinder is interrupted by the preliminary injection piston "mounted in the cylinder 12 and comprising two piston heads 13, 14, connected by a reduced stem 15. Stand off lugs 16 and 11 project from the heads 13 and 14, respectively, and limit the upward and downward movements of the piston. A coil compression spring 18 urges the piston to its upper po- A port 19 connects thespace around stein 15 with the space below head 14 and hence with passage 1 When the preliminary injection piston approaches its lowermost position (see Figure 3) the space around stem 15 exposes port 8| which previously was blanked by piston head 14, and thus connects port 8| via port 19 with passage 1|. Port 8| leads to the bore on which loading piston 62 works and at such time is blanked by piston 62.

When the preliminary injection piston reaches its lowermost position (Figure 3) its head 13 ex-- poses port 82 which leads to chamber 6|. This subjects the upper end of loading piston 62 to supply pressure delivered via tube 38, passage 68, chamber 61 and port 82, so the piston is forced down, augmenting the loading of valve 54 (Figure 3). I

Piston 62 has a peripheral groove 83 connected by slot 84 with chamber 6|. Before piston 62 reaches its lowermost position, and when it is in that position groove 83 registers with port 8| completing a connection from supply tube 38 (via 68, 61, 12,82, 6|, 84, 83, 8|, 19) to passage 1| and hence to chamber 52.

Thus, after the injection valve 54 has opened and closed as the result of the pressure surge which is developed in chamber 52 by the descent of the piston 13, 14 and dissipated by the opening of the valve 54, the valve loading is augmerited. Approximately upon the completion of such increase of loading, supply pressure is admitted directly to chamber 52. When pressure rises sufficiently to open the valve, the principal injection commences. It ends when control edge 23 exposes port l9 because the sharp but limited reflux which then occurs causes valve 54 to close sharply, inhibiting dribble.

This same reflux starts the loading piston 62 and the preliminary injection piston 13, 14 up:- u

ward, the latter closing port 82, so that the rise of piston 62 is delayed by the throttling effect of flange 69, which restricts flow past check valve 66. This action is useful in two respects: (1) it delays relief of the extra load, assuring maintained closure of the valve. (2) It assures supply of fuel from chamber 6| via 84, 83, 8|, 19 to the space below head 14, until head 14 rises far enough to lap port 8|. The effect is to convey a charge of fuel below head 74 preparatory to the next preliminary injection. Pressure on this charge is relieved by continued upward motion of piston 73, 14.

The timing of parts cannot be stated precisely without elaborate discussion of inertia effects, throttling eifects, and resulting pressure difierentials, all of which enter the problem, but the above discussion gives the general factors. Suffice it to say that the device when constructed as illustrated and described operates satisfactorily, and in the manner generally described.

The embodiment shown in Figure 4 is functionally similar but somewhat simpler to construct. Functionally similar parts are given the reference numerals used for similar parts in Figures 1-3, with the distinguishing letter a. Parts which are of distinctive form or function are given new reference numbers.

The injection valve unit is mounted in a bore 430 in cylinder head 41a and seals against shoulder 45a. The nozzle member 41a, loading spring housing 48a, cylinder member 49a and inlet cap |a are held together by two sleeves 44a and 46a, each threaded on housing 48a. The parts 52a to 64a are essentially the same as similarly numbered parts. The stop 65a. for-the loading piston takes the form of lugs in a reduced extension at the upper end of the piston. These lugs limit motion in both directions. There is no check valve such as parts 66, 69, and no chamber such as 61. Passage 68a, passage Ha, cylinder 12a and port 82a, all correspond with similarly numbered parts in Figures 1 to 3, passage 68a leading directly to the upper end of cylinder 12a.

The loading piston 62a is larger in diameter than plunger 56a and has no ports such as 83 and 84. When piston 62a is moved down to its loading position, it exposes to the interior of chamber Bla a port 85. Port 85 leads to an arcuate port 86 which curves around chamber 58a and communicates directly with passage Ha and hence with chamber 52a. Ports 85, 86 thus replace ports 8! and 19 of Figures 1-3 and perform the same ultimate functions.

The prelimirfiry injection piston 87 in cylinder 120. performs the functions of the preliminary injection piston l3, 74, of Figures 1 to 3- and also the functions of check valve 66, 69. Consequently it is of distinctive form.

The piston proper 81 makes a liquid tight sliding fit in cylinder 72a over that part of piston below shoulder 88. Above that shoulder there is a slight clearance 89 which is exaggerated in the drawings since it is too small to bevisible if drawn to true dimension. The piston has standoff bosses 9|, 92 on its ends to limit its upward and downward motion. The normal position of the piston is up but no return spring similar to spring 18 of Figures 1-3 is required.

When the piston is up, shoulder 88 is immediately below port 820. so that flow between passage 68a and port 82a is throttled by the small clearance at 89. This throttling diminishes as the piston 8'! moves down and ends by the time the piston 81 reaches its lowermost position.

upon consideration of the cycle.

The injection mechanism of Figure 4 is to be used with a pump such as the pump A of Figure 1. Except for the provision for means to ensure a definite reflux, this pump is conventional. Any pump of similar delivery characteristics may be substituted in connection with any embodiment of the invention.

With the embodiment of Figure 4, when the pump starts to deliver fuel through pipe 38a, piston-81 makes it downward displacement stroke before much fuel can reach port 82a. Hence preliminary injection takes place substantially'as described for Figures 1-3. I

When port 820. is fully open, piston 62a moves down loading the injection valve and ensuring its closure. Motion of the piston connects passages 68a and Ha (via 82a, 85, 86) and the main injection starts when supply pressure is sufficient to overcome the loading.

When supply pressure drops and the limited reflux occurs, the piston 81 moves up, so that the throttling clearance at 89 delays the rise of the jloading piston while the lowered pressure in chamber 52a causes sharp closure of valves 54a. As piston 62a rises fuel fiows via passages 85, 86 to the space below piston 81 to form a charge for the next preliminary injection.

While it is preferred thatpiston 8! make a liquid tight fit in cylinder 12a below shoulder 88, it will operate with a leaky fit throughoutits length, in which event the shoulder 88 would virtually disappear. The displacing action of the piston and its timing effect on port 82a will occur despite moderate leakage as will be obvious Thus the effects of Wear or initial loose fitting are not serious, a fact which contributes to sustained operative life and economy of manufacture.

What is claimed is:

1. In a fuel injection device, the combination of a fuel injection valve; yielding means biasing said valve in a closing direction; a movable abutment subject to the pressure of fuel delivered to the fuel injection valve and connected with the valve to open the same in response to rising fuel pressure; a fuel pump having a discharge connection, the pump being adapted to force fuel under pressure periodically through said connection and at the termination of each periodic discharge to cause a limited reflux; a preliminary injection piston interposed in a connection between said pump discharge and said injection valve; means limiting the range of reciprocation of said piston; a movable loading abutment for increasing the loading effect of said yielding means; valve means having an opening characteristic upon motion of said preliminary injection piston toward said injection valve and serving to control admission of .fuel from said discharge connection to act on the loading abutment; valve means opened by the loading movement of the loading abutment to open a normally closed path from said discharge connection to said injection valve; and flow restricting means effective upon the occurrence of reflux to permit delay dissipation of pressure acting on said loading abutment.

2. The combination defined in claim 1 in which the loading abutment and preliminary injection piston are assembled with the injection valve in a self-sustaining unit.

3. In a fuel injection device, the combination of a fuel injection valve; yielding means biasing said valve in a closing direction; a movable abutment subject to the pressure of fuel delivered to the fuel injection valve and connected with the valve to open the same in response to rising fuel pressure; a fuel pump having a discharge connection, the pump being adapted to force fuel under pressure periodically through said connection and at the termination of each periodic discharge to cause a limited reflux; a preliminary injection piston interposed in a connection between said pump discharge and said injection valve; means limiting the range of reciprocation of said'piston; a movable loading abutment for increasing the loading effect of said yielding means; means for limiting the movement of said loading abutment; valve means having an opening characteristic 'upon motion of said prelima fuel injection valve; yielding means biasing said valve in a closing direction; a movable abutment subject to the pressure of fuel delivered to the fuel injection valve and connected with the valve to open the same in response to rising fuel pressure; a fuel pump having a discharge connection, the pump being adapted to force fuel under pressure periodically through said connection and at the termination of each periodic discharge to cause a limited reflux; a preliminary injection piston interposed in a connection between said pump discharge and said injection valve; means limiting the range of reciprocation of said piston; a movable loading abutment of larger effective area than the first named movable abutment, for increasing the loading efiect of said yielding means; valve means having an opening characteristic upon motion of said preliminary injection piston toward said injection valve and serving to control admission of fuel from said discharge connection to act on the loading abutment; valve means opened by the loading move- "ment of the loading abutment to open a normally closed path from said discharge connection to said injection valve; and flow restricting means effective upon the occurrence of reflux to permit delayed dissipation of pressure acting on said loading abutment.

5. The combination defined in claim 1 in which the yielding biasing means is a spring interposed between the first named abutment and the loading abutment.

6. The combination defined in claim 3 in which the yielding biasing means is a spring interposed between the first named abutment and the loading abutment.

'1. In a fuel injection device, the combination of a fuel injection valve; yielding means biasing said valve in a closing direction; a movable abutment subject to the pressure of, fuel delivered to the fuel injection valve and connected with the valve to open the same in response to rising fuel pressure; a fuel pump having a discharge connection, the pump being adapted to force fuel under pressure periodically through said connection and at the termination of each periodic discharge to cause a limited reflux; -a preliminary injection piston interposed in a connection between said pump discharge and said injection 'closed path from said discharge connection to said injection valve; and a check valve controlling a restricted passage arranged to permit delayed reflux of fuel acting on said loading abutment to said discharge connection while inhibiting flow in the opposite direction.

8. In a fuel injection device, the combination of a fuel injection valve; yielding means biasing said valve in a closing direction; a movable abutment subject to the pressure of fuel delivered to the fuel injection valve and connected with the valve to open the same in response to rising fuel pressure; a fuel pump having a discharge connection, the pump being adapted to force fuel under pressure periodically through said connection and at the termination of each periodic discharge to cause a limited reflux; a preliminary injection piston interposed in a connection between said pump discharge and said injection valve; means limiting the range of reciprocation of said piston; a movable loading abutment for increasing the loading efiect of said yielding means; valve means having an opening characteristic upon motion of said preliminary injection piston toward said injection valve and serving tocontrol admission of fuel from said discharge connection to act on the loading abutment; valve means opened by the loading movement of the loading abutment to open a normally closed path from said discharge connection to said injection" valve; and flow restricting means associated with said preliminary injection piston for permitting 'delayed dissipation of fluid pressure acting on said loading abutment, when the pump permits reflux.

9. The combination of a fuel injection valve having a fuel chamber, discharge from which iscontrolled by said valve; yielding means urging the injection valve in a closing direction; a plunger connected with the injection valve, subject to the pressure of fuel in said chamber and arranged to urge said injection valve in an opening direction; pressure operated loading means for increasing the stress on said yielding means; a fuel pump having a discharge connection, the pump being arranged to discharge fuel'under pressure periodically through said connection and after each periodic discharge cause a limited reflux; a communication leading from said discharge connection to said fuel chamber; a. floating piston substantially obstructing said communication but capable of limited shifting motion in response to pressure impulses, said floating piston being arranged to establish free communication between said discharge connection and said loading means when the floating piston is shifted toward said chamber and at least partially obstruct such communication at other times; and means rendered effective by the loading shift of said loading means to afford a by-pass from said discharge connection around said floating piston to said chamber.

10."I'he combination of a fuel injection valve having a fuel chamber, discharge from which is controlled by said valve; yielding means urging the injection valve in a closing direction; a plunger connected with the injection valve, subject to the pressure of fuel in said chamber and arranged to urge said injection valve in an opening direction; pressure operated loading means for increasing the stress on said yielding means; a fuel pump having a discharge connection, the pump being arranged to discharge fuel under pressure periodically through said connection and after each periodic discharge cause a limited reflux; a communication leading from said discharge con nection to said fuel chamber; a floating piston substantially obstructing said communication but capable of limited shifting motion in response to pressure impulses, said floating piston being arranged to establish free communication between said discharge connection and said loading means when the floating piston is shifted toward said chamber and at least partially obstruct such communication at other times; means rendered eifective by the loading shift of said loading means to afford a by-pass from said discharge connection around said floating piston to said chamber; and restricted, one-way flow means for permitting delayed reflux of fuel from said loading means to said discharge connection.

11. The combination of a fuel injection valve having a fuel chamber, discharge from which is controlled by said valve; yielding means urging the injection valve in a closing direction; a plunger connected with the injection valve, subject to the pressure of fuel in said chamber and arranged to urge said injection valve in an opening direction; pressure operated loading means for increasing the stress on said yielding means; means for limiting the loading movement of said loading means; a fuel pump having a discharge connection, the pump being arranged to discharge fuel under pressure periodically through said connection and after each periodic discharge cause a limited reflux; a communication leading from said discharge connection to said fuel chamber; a floating piston substantially obstructing said communication but capable of limited shifting motion in response to pressure impulses, said floating piston being arranged to establish free communication between said discharge connection and said loading means when the floating piston is shifted toward said chamber and at least partially obstruct such communication at other times; and means rendered effective by the loading shift of said loading means to afford a by-pass from said discharge connection around said floating piston to said chamber.

12. In a fuel injection device, the combination of a fuel injection valve; yielding means biasing said valve in a closing direction; a movable abutment subject to the pressure of fuel delivered to the fuel injection valve and connected with the valve to open the same in response to rising fuel pressure; a fuel pump having a discharge connection, the pump being adapted to force fuel under pressure periodically through said connection and at the termination of each periodic discharge to cause a limited reflux; a movable abutment for increasing the stress on said yielding means; means operated by the motion of said abutment and serving to open in the load-increasing position of the abutment and close in other positions of the abutment a passage from said discharge connection to said injection valve; a preliminary injection piston interposed in and substantially obstructing a connection between said pump discharge connection and said injection valve, said piston being subject on one end to pressure of fuel at the pump discharge and on the other end to pressure of fuel at said injection valve and being arranged for limited reciprocatory motion in response to changes of pressure differential; and means rendered eifective by the reciprocation of said preliminary injection piston to aflord free communication from said pump discharge connection to said loading abutment when the piston is near the end .of its travel toward said injection valve and to afford controlled reflux from said abutment toward said discharge connection when the piston reverses its motion in response to reflux through said discharge connection.

BERNHARD BISCHOF.

Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US2536542 *Feb 4, 1948Jan 2, 1951Cav LtdVariable valve loading injection nozzle
US2957631 *Mar 14, 1957Oct 25, 1960Acf Ind IncNozzle for fuel injector system
US3067809 *Oct 7, 1959Dec 11, 1962Dresing FritzEquipment for the combustion of oils of differing viscosity by means of atomization in light-oil burners
US3342422 *Oct 22, 1965Sep 19, 1967Ricardo & Co EngineersFuel injection apparatus for internal combustion engines
US3392715 *Mar 17, 1966Jul 16, 1968Daimler Benz AgDevice for controlling the pre-injection
US3403861 *Mar 30, 1967Oct 1, 1968Bosch Gmbh RobertFuel injection valve for preliminary and main injection
US3465737 *Mar 26, 1968Sep 9, 1969Allis Chalmers Mfg CoFuel injection system
US3667438 *Sep 29, 1970Jun 6, 1972PeugeotFuel injecting device for an internal combustion engine
US4408586 *Jun 16, 1981Oct 11, 1983Mtu Motoren- Und Turbinen-Union Friedrichshaften GmbhFuel injection pump
US4524737 *Aug 24, 1984Jun 25, 1985Robert Bosch GmbhFuel injection apparatus with an auxiliary pump for pilot and main injection
US4590903 *Aug 24, 1984May 27, 1986Robert Bosch GmbhFuel injection apparatus for definite pilot injection and main injection in internal combustion engines
US4590904 *Jul 27, 1984May 27, 1986Robert Bosch GmbhFuel injection apparatus
US4745898 *Aug 31, 1987May 24, 1988Robert Bosch GmbhPre-injection apparatus for internal combustion engines
US4889288 *Apr 25, 1988Dec 26, 1989Lucas Industries Public Ltd. CompanyFuel injection nozzle
US6408829 *Apr 19, 2000Jun 25, 2002International Engine Intellectual Property Company, L.L.C.Fuel pressure delay cylinder
US6543706Apr 6, 2001Apr 8, 2003Diesel Technology CompanyFuel injection nozzle for an internal combustion engine
DE861345C *Sep 1, 1950Dec 29, 1952Cav LtdEinspritzduese fuer fluessigen Brennstoff fuer Verbrennungsmotoren mit federbelastetem Ventil
DE875279C *Aug 26, 1950Apr 30, 1953Cav LtdBrennstoff-Einspritzduese fuer Verbrennungskraftmaschinen
Classifications
U.S. Classification123/300, 239/88, 239/93, 123/495, 123/446, 239/533.5
International ClassificationF02M45/08, F02M57/02, F02M59/02
Cooperative ClassificationF02M2700/078, F02M59/02, F02M57/02, F02M45/08
European ClassificationF02M45/08, F02M59/02, F02M57/02