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Publication numberUS3011489 A
Publication typeGrant
Publication dateDec 5, 1961
Filing dateJan 19, 1960
Priority dateJan 26, 1959
Publication numberUS 3011489 A, US 3011489A, US-A-3011489, US3011489 A, US3011489A
InventorsBessiere Pierre Etienne
Original AssigneeBessiere Pierre Etienne
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Reciprocating action pumps for the injection of fuel into internal combustion engines
US 3011489 A
Abstract  available in
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Claims  available in
Description  (OCR text may contain errors)

- 5, 196 P. E. BESSIERE 8 RECIPROCATING ACTION PUMPS FOR THE INJECTION OF FUEL INTO INTERNAL COMBUSTION ENGINES Filed Jan. 19, 1960 w M w 0 l ax w o umw 8 a 82 0 A 5 L 7 wmw 5 J 7 n Z l g y B 2 m M a 2 7 J f; ET 2 fl rw 4 m v Z G. W

INVEN TOR nacrraocarmo ACTION PUMPS For: THE 1N JECTIGNOF FUEL INTO INTERNAL COMBUS- TIDN ENGINES Pierre Etienne Bessiere,,55 Blvd. CommandantCharcot,

. Neuilly sur-Seine, France Filed Jan. 19, 1960, Ser. No.3,335 Claims priority, application France Jan. 26', 195$ 4 Claims. (Cl. 123 139) The present invention, relates'to reciprocating action pumps for the injection of tuelinto internal combustion engines, said pumps being of the'kind where automatlc regulation of the output shuttle member, having its outward movements produced by impulses, and in particular hydraulic impulses, the frequency of which is proportional to the speed of the internal combustion engine, whereas the return movements of said shuttle member, produced bya return spring, are braked by a throttling provided in the conduit. through which must fiow a liquid brought in movement by the shuttle member during its return movements.

The object of this invention is to stop any delivery of the pump when the internal combustion engine fed with liquid by'said pump starts running in'a direction opposed to that in which it must normally run.

is ensured by apart, called The invention consists chiefly in'providing in said coud-uit a. valve member which is brought, againstthe ac tion of a return spring, into a position where it closes said outflow conduit, by a hydraulic impulse produced by a pump driven by the internal combustion engine when the'latter starts running in a direction opposed to that in which it must normally run. a

A preferred embodiment of the present invention will be hereinafter described with reference to the accompany,- ing drawing, which:

given merely by way of example and in The only figureof the drawing diagrammatically shows I i in axial section the main elements'of a fuel injection pump made according to the invention and combined withran auxiliary gearpurnpdriven by the engine fed with fuel by the fuel injection pump,

The fuel injection pump includes a main cylinder 1' in which is slidablytitted a main piston 2 driven by the internal combustion engine (not shown) through a cam 22. This piston controls a port 3 through which the fuel feed conduit 4 opens into cylinder 1. This conduit 4 is fed from a pump (not shown) which constitutes what is called a transfer pump. Cylinder 1 communicates with a delivery conduit Sleading toward theinjector or injectors of the engine, a check-valve 6 being mounted in said delivery conduitS.

3,011,489 Patented Dec. 1961 ice injected, delivered by an auxiliary reciprocating pump drivenin synchronisrn with'the main pump. Advantageously, as shown by the drawing, this auxiliary pump is constituted by providing the main piston 2, on the side op-- posed to the working face of the cylinder 1, withan extension 2a oflarger diameter which is slidably mounted in a cylindrical bore 1a of corresponding diameter. The "annular space 17 formed between said bore in and piston 2 is connected through a conduit 18, provided with a check-valve 24, with a cylinder 11 in which shuttle member 8 is slidably mounted. Furthermore, said an nular space 17 -is connected through a feed conduit 19 t0 rated at such a level that itfis closed, at least partly, by

shuttle 8 during the same time as discharge conduit 7 is itself closed by the shuttle'membensaid discharge conduit 20'being wholly opened atthe earliest at the time p when thedischarge conduit 7 is itself wholly open.

The braking system above referred to is constitutedby a conduit 12 provided with a throttle pass-age 13 through which the shuttle member forces back liquid during the return strokes of said shuttle member.

As soon asshuttle member. 8 has moved a distance a in the upward direction under the action of the liquid delivered by piston 2a into auxiliary cylinder 11," it connects, through annular groove 25, the two portions of thedis-charge conduit 7, whichstops the delivery of fuel by piston 2 into delivery conduit 5. I

When piston 2, 2a starts moving back in the'downward direction, shutle member 8,-under theactio'n of a "return spring '19, also starts moving moving downin its also piston 2, 2a rea'ch-a given speed, shuttle member 8,

due to said braking action, is no longer capable of reachmg its lowermost position, where it is applied against an abutment 40, before piston 2, 2a starts back moving upwardly. Thus, the return stroke of the shuttle member is shortened and the opening of discharge conduit 7 takes place for delivery strokes-of piston 2, 2a.which are the In order to obtain an automatic regulation of the a delivery flow rate of the pump, that is to say of the amount of fuel which flows through conduit 5 on every cycle of the pump, as a function'of the speed, and for speeds exceeding a given limit, 11 provide cylinder 1 with a dis--. charge conduit 7 controlled by a shuttle member 8. This shuttle member 8 is driven through hydraulic means in one direction (outward strokes, that is to say upward i the drawing). Shuttle member 8 is returned'in the op- .posed direction (return stroke), during every suction stroke of piston 2, by a return device' against the action of a braking system which will be hereinafter disclosed. The

The hydraulic means for producing the upward strokes return device is preferably constituted by a spring Ill. 7

shorter as the speed increases more and more; I thus obtain a corresponding reduction in the delivery flow rate about its axis and having an oblique end face 58a. When member 5% isrotated about its axis, thecross-section "area of the throttled poition 13 of conduit 12 is varied.

Furthermore, this member 50 is provided with a dis-' charge conduit 51 extending therethrough and which, for the position of member 59 wherethe cross-section area of throttled passage 13 is minimum. (and may be equalto zero), is placed in communication with a discharge conduit 52, thus permitting shuttle 8 to remain, during the values of the cross-section area of thethrottled passage I which may in particular happen when said engine is started with an excessive lead to ignition, shuttle member 8 is to be blocked into its uppermost position where it keeps discharge conduit 7 permanently open. This result is obtained by means of a slide valve 53 which is then brought into a position where it wholly closes conduit 12, such a movement of valve 53 being produced by a hydraulic.

impulse supplied by a pump driven by the internal combustion engine when said engine starts running in the di rection opposed to that in which it should normally run.

Of course, when there is provided, on conduit 12, a by-pass conduit 51, 52 intended to be opened just when the internal combustion engine is being started, valve member 53, in its closing position, must close not only the branch of conduit 12 through which liquid is returned from cylinder 11 to cylinder 1a, but also said by-pass conduit 51, 52. v

Advantageously, the pump which supplies the hydraulic impulse intended to actuate valve 53 is a gear pump 54 the intake pipe 55 of which is connected, through a conduit 56, with a cylinder 57 in which the end of valve 53 is slidably mounted. As long as pump 54 runs in the normal direction indicated by the arrows it does not produce a hydraulic impulse in cylinder 57 so that a spring 58 acts upon valve 53 to keep it' in the position where the grooves provided therein keep conduit 12 and conduit 52 open. On the contrary, as soon as the internal combustion engine starts running in the wrong direction and therefore causes-pump 54 also to run in the direction opposedto that in which it should normally run, this pump 54 sends a hydraulic impulse into cylinder 57, which causes valve 53 to move toward the right and therefore to close conduit 12 and conduit 52. Shuttle member 8 is thus prevented, after it has been once moved, as a consequence of the delivery stroke of piston 2, 2a, into its uppermost position where it opens discharge conduit 7, from returning toward its lowermost position. Valve 53, when it has been brought into the position where it closes conduits 12 and 52, opens a discharge orifice 59 through which the liquid fed from the conduit 56 can escape from chamber 57.

i What I claim is': 1 1. For use with an internal combustion engine, a reciprocating action fuel pump which comprises, in combination, a pump cylinder, a piston adapted to cooperate with said cylinder mounted for reciprocating movement therein,

-so as to limit therewith a variable volume working space,

the movements of said piston in said cylinder in the direction for which the volume of said working space is reduced being called delivery strokes, a casing rigid'with said cylinder, a shuttle member fitting movably in said casing so as to limit with the innerwall thereof a variable volume chamber, means for constantly keeping said chain ber filled with liquid, the movements of said shuttle member in said casing in the direction for which the volume of said chamber is increased being called outward strokes and the movements of said shuttle member in the opposed direction being called return strokes, means operative'by said piston for producing outward strokes of said shuttle member in synchronism with the delivery strokes of said piston, resilient means interposed between said casing and said shuttle member for urging said shuttle member in the direction to produce the return strokes of said shuttle member, a fuel delivery conduit leading to the internal combustion engine to be fed by the pump, a fuel circulation circuit including said working space of said cylinder and leading to said delivery conduit, said casing being connected with said fuel circulation circuit so that said shuttle member controls, in accordance with the amplitude of its reciprocating movement in said casing, the amount of fuel fed to said delivery conduit on every delivery stroke of said piston, a conduit starting from said variable volume chamber for the outflow of liquid therefrom during the return strokes of said shuttle member, means in said liquid outflow conduit for throttling a portion thereof, to slow down said liquid outflow and thus to exert on said shuttle member, during its return strokes, a braking action such that, for speeds of operation of the pump above a given value, said shuttle member return strokes are the shorter as the speed of operation of the pump is higher, a hydraulically controlled valve mounted in said liquid outflow conduit for controlling the flow of liquid therethrough, resilient means operatively engaging said valve for urging said valve toward conduit opening In order to enable auxiliary pump 54 to feed liquid through conduit 56 with a .sufficient pressure, when the direction of rotation of pump 54 is reversed, I provide in intake conduit 55, upstream of the point where the conduit 56 branches oft" therefrom, a check-valve 60 which opens in the direction toward pump 54.

Gear pump 54 may be for instance the transfer pump above referred to and which has its output connected with conduits 4 and 19. According to a preferred embodiment of the present invention, this pump 54 belongs to a hydraulic speed governor. 1 In the embodiment which has just been described, the shuttle member keeps in the open state a discharge co n.

duit 7 connected with the cylinder 1 of the pump (said discharge conduit might also be connected with delivery conduit 5) and thus prevents any flow of fuel toward the injector or injectors as soon as the internal combustion engine starts running in a direction opposed to that in which it should run.

In a general manner, while I have, in the above description, disclosed what I deem to be practical and efiicient embodiments of my invention, it should be well understood that I do not wish to be limited thereto as there might be changes made in the arrangement, disposition and form of the parts without departing from the principle of'the present invention as comprehended within the scope of the accompanying claims.

position, hydraulic means for moving said valve into conduit closing position in response to a hydraulic impulse transmitted to said hydraulic means and pumping means driven by the internal combustion engine to be fed by the pump, said pumping means being arranged to send a hydraulic impulse to said valve when said internal combustion engine starts running in the direction opposed to that in which it is to run normally.

2. A pump according to claim 1 further including a A by-pass conduit leading out from said variable volume chamber of said casing, means for adjusting the crosssection area of said outflow conduit throttled portion, said adjusting means being capable of controlling said by-pass conduit so as normally to keep it closed and to I open it only when said throttle portion cross-section area is minimum, said hydraulically controlled valve being 'mounted to close said bypass conduit at the same time as it closes said liquid outflow conduit.

3. A pump according to claim 1 comprising means forming a cylindrical housing closed at one end and fixed with respect to said liquid outflow conduit, said hydraulically controlled valve being a slide valve fitting slidably in said housing, said closed end of said housing and the corresponding end of said slide valve limiting between them a variable volume space, said pumping means consisting of a continuous rotation auxiliary pump having a pipe which constitutes its intake pipe when said auxiliary pump is driven by said internal combustion engine running in its normal direction, conduit means for connecting said pipe with said variable volume space and a check-valve in said pipe opening toward said auxiliary 6 v pump and located in the portion of said pipe, acting as 4. A pump according to claim 3 in which said housintake pipe, upstream of the point Where said conduit ing is provided, in the wall thereof cleared by said slide a means branch off therefrom, whereby, in case of said valve when it is in the outflow conduit closing position, engine running in the reverse direction, said auxiliary with a discharge orifice for the liquid delivered by said pump is reversed and then sends a hydraulic impulse 5 auxiliary pump. through said conduit means to said variable volume space NO references cited.

of said housing.

Non-Patent Citations
1 *None
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3385219 *Aug 11, 1966May 28, 1968Konrad EckertFuel injection pump
US3391641 *May 11, 1966Jul 9, 1968Bosch Gmbh RobertOutput regulated pump
US4387686 *Jan 27, 1981Jun 14, 1983Robert Bosch GmbhFuel injection apparatus for internal combustion engines, in particular for diesel engines
US4398518 *Jan 27, 1981Aug 16, 1983Robert-Bosch GmbhFuel injection apparatus for internal combustion engines, in particular for diesel engines
US4398519 *Jun 24, 1981Aug 16, 1983Robert-Bosch GmbhFuel injection apparatus for internal combustion engines, in particular for diesel engines
US4414947 *Jul 12, 1982Nov 15, 1983Diesel Kiki Co., Ltd.Fuel injection system for multi-cylinder internal combustion engines, having high injection pressure
US5239969 *Oct 8, 1991Aug 31, 1993Southwest Research InstituteMechanical fuel injector for internal combustion engines
U.S. Classification123/446, 123/41.00R, 417/293
International ClassificationF02M59/00, F02M63/02, F02M59/36
Cooperative ClassificationF02M2700/1317, F02M63/0205, F02M59/365, F02M59/00
European ClassificationF02M59/00, F02M59/36C, F02M63/02B