US3090314A - Self regulating reciprocating pumps and in particular fuel injection pumps - Google Patents

Self regulating reciprocating pumps and in particular fuel injection pumps Download PDF

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Publication number
US3090314A
US3090314A US106663A US10666361A US3090314A US 3090314 A US3090314 A US 3090314A US 106663 A US106663 A US 106663A US 10666361 A US10666361 A US 10666361A US 3090314 A US3090314 A US 3090314A
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Prior art keywords
piston
strokes
conduit
shuttle member
cylinder
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US106663A
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English (en)
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Bessiere Pierre Etienne
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    • 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
    • F02M41/10—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 pump pistons acting as the distributor
    • F02M41/12—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 pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—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 pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F02M41/127—Variably-timed valves controlling fuel passages valves being fluid-actuated slide-valves, e.g. differential rotary-piston pump

Definitions

  • the present invention relates to self-regulating reciproeating pumps, that is to say to pumps such that their delivery flow rate per cycle, at least for speeds above a given speed, decreases as this speed increases.
  • the invention is more especially concerned with fuel injec tion pump for internal combustion engines.
  • pumps of the above InentiOned kind having a mechanically driven reciprocating piston arranged to produce through hydraulic means, during every outward, or delivery, stroke thereof, a corresponding outward stroke of a regulating member, called shuttle, preferably in the form of an auxiliary piston, whereas, during at least a portion of the period elapsing between the beginning of every return stroke of said piston and the beginning of its next outward stroke thereof, this shuttle member, moving on its own return stroke under the action of a return force, supplied for instance by a spring, expels liquid through a throttled passage, which exerts a braking effect on said shuttle member.
  • a mechanically driven reciprocating piston arranged to produce through hydraulic means, during every outward, or delivery, stroke thereof, a corresponding outward stroke of a regulating member, called shuttle, preferably in the form of an auxiliary piston, whereas, during at least a portion of the period elapsing between the beginning of every return stroke of said piston and the beginning of its next outward stroke thereof, this shuttle member, moving
  • the shuttle member which preferably controls a discharge, or by-pass, conduit for the outflow of the liquid present in the working space of the pump, no longer returns to its position of rest from which it starts normally to make its outward strokes, but is stopped before reaching this position by what is called a liquid abutment whereby its outward strokes are more and more shortened, thus reducing more and more the delivery flow rate of the pump as the speed at which the ptunp is driven exceeds more and more said given value.
  • the object of the present invention is to eliminate this drawback.
  • a mechanically driven valve mounted in series with said check valve and operated to be opened just before said check valve is normally to open and to be closed just after said check valve is normally to be closed.
  • FIG. 1 shows in vertical section a fuel injection pump made according to the invention.
  • FIG. 2 is a sectional view on the line II-II of FIG. 1.
  • FIG. 3 is a view similar to FIG. 1 and showing a modification.
  • the fuel injection pump comprises a main cylinder 1, in which is slidably mounted a main piston 2 which is given a reciprocating axial movement by a cam (not shown) or any suitable driving means operated by the engine to be fed with fuel by the pump.
  • This piston 2 closes, at the beginning of every outward, or delivery, stroke (upward stroke in the example shown) a port 3 through which a fuel feed conduit opens into cylinder 1, this feed conduit being supplied with fuel by a pump not shown and usually called transfer pump.
  • From cylinder 1 starts at least one delivery conduit 4 provided with a check valve 5 and leading to an injector (not shown).
  • a discharge or by-pass conduit 6 starts from cylinder -1, so that when this discharge conduit is opened the pump ceases to deliver fuel through conduit 4 toward the injector.
  • the opening and closing of this conduit 6 are controlled by a regulating member, called shuttle, in the form of an auxiliary piston 7 movable in a cylinder 8 and provided with an annular groove 9.
  • shuttle 7 When shuttle 7 is in the position where this groove 9 connects together the two portions of discharge conduit 6 (which opens at different respective levels into cylinder 8) the discharge conduit is open and the fuel delivered by piston 2, instead of passing into delivery conduit 4, passes through conduit 6 to be returned for instance to a fuel tank.
  • Shuttle 7 is arranged and controlled in such manner that when the speed at which the piston 2 of the pump is driven exceeds a given value, it opens discharge conduit 6, during every upward stroke of piston 2, earlier and earlier (thus reducing the flow rate of the pump for every delivery stroke), as the speed at which piston 2 is driven increases above said given value.
  • shuttle 7 is hydraulically driven in the direction of its upward strokes, which correspond to the delivery stroke of piston 2, by liquid delivered by an auxiliary piston 10 moving in synchronism with piston 2.
  • this auxiliary piston 10 consists of a portion of enlarged diameter of piston 2, this auxiliary piston 10 being slidable in an auxiliary cylinder 11.
  • Liquid which may for instance consist of fuel, is admitted into cylinder 11 through a feed conduit 12 closed as piston 10 is starting on its upward stroke, and this liquid is fed to the bottom end of cylinder 8 through a conduit 13 which permits the passage of the liquid only from cylinder 11 toward cylinder 8 but not in the opposed direction.
  • the outward (upward) stroke of shuttle clears a discharge conduit 14 opening into cylinder 8.
  • shuttle 7 pushed back by spring 15, reaches its position of rest determined by an abutment 19 (preferably adjustable), despite the braking effect of throttled passage 17, before pistons 2 and start back on the next upward stroke. Consequently, for speeds below this value the amplitude of the shuttle stroke is maximum and the amount of fuel delivered by piston '2 through delivery conduit 4 is also maximum. However, when the speed of the pump exceeds this given value, shuttle 7 is no longer capable of returning into its position of rest, is.
  • shuttle 7 depends upon the liquid tightness of the means that prevent back flow of liquid through conduit 13.
  • Check valve 20, which constitutes said means may in some cases be insufficiently liquid tight. This is why, according to the present invention, it provide in series with check valve 20, a mechanically driven valve working in synchronism with pistons 2 and 16 so as to open conduit 13 shortly before the time when check valve 253 normally opens this channel, and to close said channel '13 shortly after the time when check valve is normally to close it.
  • check valve 29 is not modified by the presence of the mechanically driven valve which is substituted for this check valve only in case of failure of the check valve to operate normally, this failure being generally of short duration (some seconds) so that the slight increase of the time of opening of conduit 13 which results from the action of the mechanically driven valve cannot produce any serious perturbation in the operation of the engine.
  • the mechanically driven valve may be a slide valve having a reciprocating longitudinal movement to control conduit 13.
  • this valve is preferably a rotating valve.
  • piston 2 or of auxiliary piston 10, rigid therewith it is particularly advantageous to make use of piston 2 or of auxiliary piston 10, rigid therewith, to constitute the mechanically driven valve which controls conduit 13.
  • piston 2 or piston 16 should be given a movement of rotation about the axis thereof and this is especially advantageous when piston 2 has a rotating movement to act as a distributing valve sending fuel toward diiierent injectors during successive delivery strokes.
  • auxiliary piston 10 acts as a rotating valve to control the opening and closing of conduit 13 whereas piston 2 acts as a distributing valve to send the fuel delivered by the pump to the different injectors successively.
  • Both of the pistons form a single piece having both a reciprocating longitudinal movement and a movement of rotation about its axis. This movement of rotation is produced by means well known in the art of fuel injection pumps and not shown by the drawings.
  • the side wall of cylinder 1 there is provided, at a level higher than that of feed conduit 3, a plurality of (for instance four) delivery conduits 4, each provided with a check valve 5 and leading to a corresponding injector.
  • the side wall of piston 2 is provided, in the upper portion thereof, with a longitudinal groove 22 which, during the successive delivery strokes of piston 2 cyclically connects the working chamber of the pump with the respective delivery conduits 4.
  • the working chamber of the pump is filled with fuel from feed conduit 3 through an annular groove 23 provided in the side Wall of piston 2 and which communicates with the working chamber of the pump through an axial conduit 24.
  • this arrangement of grooves 25 has the further advantage of permitting the inflow of liquid into auxiliary cylinder 11 during the whole return stroke of pistons 2 and ill. Furthermore, it tends to apply pistons ltl and 2 against the cam by which they are driven since feed pressure in cylinder 11 urges piston 10 in the downward direction.
  • FIG. 3 shows the lower portion of a pump made according to a modification of that shown by FIGS. 1 and 2.
  • grooves 25 formed in auxiliary piston 10 serve to control both feed conduit 12 and conduit 13.
  • the grooves 25a provided in the side wall of piston 10 serve only to control feed conduit 12, whereas the opening and closing of conduit 13 is controlled by grooves 26 provided in the side wall of piston 2.
  • 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, and those in the opposed direction return strokes, a casing rigid with said cylinder provided with a discharge port opening to the outside, a shuttle member adapted to control said dis charge port, said shuttle member fitting movably in said casing so as to limit with the inner wall thereof a variable volume chamber, 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, a fuel delivery means, conduit means in said casing including a connection from said working space to said fuel delivery means and a connection to said variable volume chamber and conduit means providing an outflow for liquid from the variable volume chamber, means operative by
  • a self-regulating liquid pump which comprises, in combination, a main cylinder, a main piston fitting slidably in said cylinder, so as to limit therewith a variable volume Working space, means for reciprocating said piston in said cylinder, a delivery conduit in communication with said cylinder working space, means forming a housing having at least one cylindrical portion, a discharge conduit leading from said cylinder working space to the outside and including a portion of said housing, a reciprocating shuttle piston having a cylindrical portion thereof fitting slidably in said cylindrical portion of said housing so as to form therein a slide valve controlling the opening and closing of said discharge conduit, said shuttle piston limiting, together with said housing, a variable volume chamber so that variation of the volume of said chamber corresponds to a movement of said shuttle piston in said housing, an auxiliary reciprocating pump operatively connected with said main piston so as to work in synchronism therewith, conduit means for connecting the delivery of said auxiliary pump with said variable volume chamber so as to move said shuttle piston in said housing in one direction in response to every delivery stroke of said auxiliary pump
  • a self-regulating liquid pump which comprises, in combination, a main cylinder, a main piston fitting slidably in said cylinder, so as to limit therewith a variable volume Working space, means for reciprocating said piston in said cylinder and rotating it about its axis, a delivery conduit in communication with said cylinder working space, means forming a housing having at least one cylindrical portion, a discharge conduit leading from said cylinder working space to the outside and including a portion of said housing, a reciprocating shuttle piston having a cylindrical portion thereof fitting slidably in said cylindrical portion of said housing so as to form therein a slide valve controlling the opening and closing of said discharge conduit, said shuttle piston limiting, together with said housing, a variable volume chamber so that variation of the volume of said chamber corresponds to a movement of said shuttle piston in said housing, an auxiliary reciprocating pump comprising a portion of enlarged diameter of said main piston and an auxiliary cylinder arranged to cooperate with said enlarged piston portion, conduit means for connecting the said auxiliary cylinder with said variable volume chamber so as to move said shuttle piston
  • a pump according to claim 4 including :a plurality of delivery conduits starting from different points of said main cylinder located in different radial planes thereof, respectively, the portion of said piston located in said main cylinder acting as distributing means for feeding fuel to said respective delivery conduits respectively on successive strokes of said piston, said portion of enlarged diameter of said piston being provided with several longitudinal grooves to cooperate with said conduit means to form said mechanically driven valve, and at least one feed conduit opening into said auxiliary diameter to cooperate with said groove to control the inflow of liquid into said auxiliary cylinder during the return strokes of said piston.
  • a pump according to claim 7, comprising a number of feed conduits equal to the number of said longitudinal grooves.

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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)
  • Reciprocating Pumps (AREA)
US106663A 1960-05-11 1961-05-01 Self regulating reciprocating pumps and in particular fuel injection pumps Expired - Lifetime US3090314A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR826877A FR1267896A (fr) 1960-05-11 1960-05-11 Perfectionnements apportés aux pompes alternatives autorégulatrices, notamment pour l'injection de combustible dans les moteurs

Publications (1)

Publication Number Publication Date
US3090314A true US3090314A (en) 1963-05-21

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US106663A Expired - Lifetime US3090314A (en) 1960-05-11 1961-05-01 Self regulating reciprocating pumps and in particular fuel injection pumps

Country Status (5)

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US (1) US3090314A (fr)
DE (1) DE1153940B (fr)
ES (1) ES267279A1 (fr)
FR (1) FR1267896A (fr)
GB (1) GB970729A (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3320893A (en) * 1965-05-14 1967-05-23 Bosch Gmbh Robert Regulated injection pump
US3385219A (en) * 1965-08-12 1968-05-28 Eckert Konrad Fuel injection pump
US3391641A (en) * 1965-05-14 1968-07-09 Bosch Gmbh Robert Output regulated pump

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE560590A (fr) * 1956-11-06
AT210668B (de) * 1957-12-21 1960-08-25 Pierre Etienne Bessiere Selbstregelnde Kolbenpumpe, insbesondere zur Brennstoffeinspritzung in Motoren

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3320893A (en) * 1965-05-14 1967-05-23 Bosch Gmbh Robert Regulated injection pump
US3391641A (en) * 1965-05-14 1968-07-09 Bosch Gmbh Robert Output regulated pump
US3385219A (en) * 1965-08-12 1968-05-28 Eckert Konrad Fuel injection pump

Also Published As

Publication number Publication date
FR1267896A (fr) 1961-07-28
ES267279A1 (es) 1961-11-16
DE1153940B (de) 1963-09-05
GB970729A (en) 1964-09-23

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