US3620647A - Fuel injection system for internal combustion engines - Google Patents

Fuel injection system for internal combustion engines Download PDF

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Publication number
US3620647A
US3620647A US63071A US3620647DA US3620647A US 3620647 A US3620647 A US 3620647A US 63071 A US63071 A US 63071A US 3620647D A US3620647D A US 3620647DA US 3620647 A US3620647 A US 3620647A
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US
United States
Prior art keywords
control member
bypass
pump
piston
fuel
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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.)
Expired - Lifetime
Application number
US63071A
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English (en)
Inventor
Gerald Hofer
Heinz Nothdurft
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated

Definitions

  • the invention relates to a fuel injection system for internal combustion engines.
  • a system of this type is known in which the amount or rate of fuel supply is variable in dependence on the r.p.m. by interruption of the delivery at least upon attainment of the maximum r.p.m. owing to the opening of a first bypass of the injection pump work chamber during the pressure stroke of the pump piston by means of a reciprocating control member, which is driven during its pressure stroke by the pressure liquid supplied from an auxiliary pump operating in synchronism with the injection pump, and which is decelerated during the return stroke thereof by means of a throttle channel having a restriction through which at least a portion of the liquid supplied during the pressure stroke is made to flow during the return stroke, whereby the control member upon the attaining of a predetermined rpm.
  • a second bypass conduit being provided for the work chamber and which is controlled by the control member and by a slide valve operating in synchronism with the injection pump and with the auxiliary pump.
  • a fuel injection system of this type is known from German Pat. No. 1,286,804, in which the second bypass is blocked by the control member during the starting process and also as long as the control member returns to its initial position or the fluid abutment has not reached a predetermined level, the second bypass conduit is opened up by the pump piston before the control member opens the first bypass.
  • a means is provided in the known fuel injection system for preventing the pressure liquid supplied by the auxiliary pump and flowing off through a release channel serving to supply an additional amount of fluid during the starting process from disturbing the control process within the range of r.p.m. corresponding to full loading.
  • the essential feature of the invention consists in a dimensioning of the system, whereby the second bypass is opened up by the control member before the first bypass, and, when no fluid abutment is present, is closed by the slide valve before the opening in response to the control member, whereas in the presence of a fluid abutment it is opened up by the control member at an increasingly earlier time relative to the closing thereof by the slide valve as the level of the fluid abutment rises.
  • FIG. 1 is a longitudinal section through an embodiment of the fuel injection system according to the invention.
  • FIG. 2 shows diagrams illustrating operation of the system of FIG. 1.
  • numeral 1 represents the housing of a fuel injection pump.
  • housing 1 is a cylinder 3 with a combined slide valve and piston 2 reciprocable therein and delimiting therewith a work chamber 4.
  • Piston 2 is reciprocated and at the same time rotated about its axis by means known per se and not shown in the drawing.
  • work chamber 4 is supplied with fuel from a suction chamber 5 via a suction boring 6 and one of a number of longitudinal notches 7 on piston 2, an annular notch 8, an axial boring 9, which communicates with annular notch 8 and a transverse boring l0.
  • Piston 2 supplies fuel via a distributing notch 1 1 successively to supply conduits 12, in each of which there is provided a nonretum valve 13 with a pressure release piston 13, conduits 12 being connected to pressure lines not shown, which connect with the individual injection valves of the engine.
  • the release and nonretum valve 13 prevents in known manner the occurrence of a spurious delayed injection due to pressure variation or elasticity in the pressure line or to the compressibility of the fuel, and which might otherwise tend to occur after the termination of the actual injection process.
  • Longitudinal notches 7, only two of which are shown, and supply conduits 12, of which only one is shown, are spaced uniformly about the circumference of piston 2 and boring 3 in a number equal to that of the cylinders of the engine.
  • Control member 14 operates in a cylinder 15 and controls the connection between a bypass channel section 16a connecting work chamber 4 with cylinder 15, on the one hand, and a bypass channel section 16b connecting cylinder 15 with suction chamber 5, on the other hand.
  • Control member 14 has an annular notch 17 which is in continual connection with channel section 16a and in the inoperative position of control member 14 shown in FIG. 1 is disconnected from section 16b.
  • a section of larger diameter of piston 2 forms the piston 18 of an auxiliary pump.
  • Piston 18 operates in a cylinder 19.
  • the liquid displaced by piston 18 displaces control member 14 during its operative stroke.
  • Connecting with the end surface space of piston 18 are longitudinal notches 20 provided on the cylindrical surface thereof in the same number and in the same planes as longitudinal notches 7.
  • piston 18 displaces fuel substantially via longitudinal notches 20 and a channel 22 into cylinder 15 below control member 14.
  • Channel 22 and suction borings 21 are disposed in staggered arrangement.
  • control member 14 As control member 14 is displaced by the fuel supplied from the auxiliary pump just before the end of its operative stroke it interconnects bypass channel sections and 16b.
  • the inoperative position of control member 14 is determined by a stop 23 disposed at the lower end of cylinder 15.
  • control member 14 is driven by a return spring 24 and displaces at least a portion of the liquid which was supplied during the operative stroke via a channel 25 back into cylinder 19, channel 22 being held closed by a nonretum valve 26.
  • Interposed in channel 25 is a cylinder 27, in which a slide valve 28 is axially displaceable by means of a screw 29.
  • Slide valve 28 has a peripheral notch 30, in which terminates the section of channel 25 connected with the cylinder of piston 15, whereas the section connecting with cylinder 19 can be throttled at 31 by slide valve 28.
  • control member 14 The return movement of control member 14 is braked in dependence upon the cross section of the throttling restriction 31. Above a certain r.p.m. determined by the cross section of restriction 31, the pressure stroke of the auxiliary pump sets in before control member 14 has returned to its initial position abutting stop 23. Due to this fluid abutment" provided for control member 14, it begins its forward stroke from another initial position, whereby bypass sections 16a and 16b are interconnected at an earlier time during the displacement stroke. This leads to a decrease in the amount or rate of injection and consequently also in the r.p.m. of the engine supplied from the fuel injector.
  • the operative stroke of control member 14 ends in any event when the lower end thereof opens up a safety bore 32, which connects with suction chamber 5 and through which any further amount of fuel supplied by the auxiliary pump can drain ofl.
  • bypass channel 33 Before the opening of channel 16b by control member 14, the latter opens up a second bypass channel 33, which also connects with suction chamber 5, however, bypass channel 33 has interposed therein cylinder 3, in which piston 2 operates.
  • annular notch 34 Provided on the cylindrical surface of piston 2 is an annular notch 34 for controlling second bypass channel 33 and holding it open as long as piston 2 is in its lower inoperative position, but disconnecting it therefrom when the piston has gone through a certain portion of its pressure stroke.
  • the length of this portion of the stroke required for blocking channel 33 is selected in such a way that at full loading, i.e., as long as control member 14 returns to its initial position on stop 23, channel 33 is closed by piston 2 before control member 14 has opened up the same.
  • channel 33 is opened up by control member 14 before the pump piston has gone through the corresponding portion of its stroke. Therefore, a portion of the fuel displaced by piston 2 flows via bypass section 16a, annular notch 17, and second bypass channel 33 into suction chamber 5 until channel 33 is closed by piston 2.
  • FIG. 2 a pair of diagrams are shown one above the other.
  • the upper diagram represents the displacement s,, of control member 14 as a function of the angle of rotation at of the driving means, usually in the form of a cam, causing the reciprocating movement of piston system 2, 18.
  • the lower diagram represents the displacement s of piston 2, 18 or the corresponding amount Q of liquid displaced by piston 2, also as a function of angle a.
  • the lower diagram shows a curve V illustrating the sinusoidal movement of piston system 2, 18.
  • the horizontal line 8 indicates the displacement of control member 14 from fixed stop 23 which is required for second bypass channel 33 to open (intersections of line S with characteristics I to IV).
  • the horizontal line 51s shows the displacement required by control member 14 i for first bypass section 16b to open up (intersections of line 8,,
  • Characteristics I shows the movement of control member 14 as long as it is able on its return stroke to attain the inoperative position on stop 23.
  • Characteristics II to IV show the movement of control member 14 for different increasing levels 8,, S and S of the fluid abutment.
  • the horizontal line 8,, of the lower diagram shows the position of the pump piston at which the connection of suction borings 6 and 21 is brought about by pistons 2 and 18, respectively, and the forward stroke of control member 14 begins. This position corresponds to the angle a At the angular position 01, when the pump piston system is in the position S annular notch 34 is disconnected from second bypass channel 33 and the latter is blocked.
  • the amount of fuel delivered by injection pump piston 2 can be thought of as consisting of two portions, namely, the quantity q 1 which is delivered between positions a and cr fintersection a S;,) and the quantity 4 g, delivered between positions a, and a,,( intersection a S
  • the pump is designed in such a manner that the first quantity q delivered between 5,, and S which is comparatively small, serves to compensate for the loss of volume occurring when the fuel pressure line is drained through piston 13' of nonretum valve 13, whereas the second quantity is the effective amount of fuel injected. In the entire range of r.p.m. corresponding to full loading, the ratio of these quantities is maintained constant.
  • control member 14 opens up safety bore 32 at S which controls the maximum stroke thereof. After the opening of safety bore 32, characteristic IV is horizontal and then drops, just extent the other characteristics, from position a on.
  • the initiation of the injection is retarded within the range of downward regulation, and this takes place to a greater extent as the load decreases, i.e. the r.p.m. increases.
  • nonreturn valve 13 with its release piston 13' is replaced with a nonretum valve without such piston, there takes place in the region of partial loading or idling a preinjection by the quantity q h which may contribute to smooth running in the idling state.
  • a fuel injection system for internal combustion engines having a variable rate of fuel supply in dependence on the r.p.m. comprising,
  • a fuel injection pump having a cylinder and a pump piston in said cylinder delimiting therewith a work chamber
  • a reciprocable control member for interrupting the delivery of said pump at least at maximum r.p.m. by opening up said first bypass during the pressure stroke of the said pump piston
  • a throttle channel having a controllable restriction therein and connected to receive a portion of the liquid displaced during the return stroke of said control member, thereby to decelerate said return stroke
  • a second bypass connected with said work chamber and means on said control member for controlling said second yp a slide valve driven in synchronism with said injection pump and said auxiliary pump for controlling said second bypass,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
US63071A 1969-09-19 1970-08-12 Fuel injection system for internal combustion engines Expired - Lifetime US3620647A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1947528A DE1947528C3 (de) 1969-09-19 1969-09-19 Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE1947529A DE1947529C3 (de) 1969-09-19 1969-09-19 Kraftstoff einspritzpumpe für Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
US3620647A true US3620647A (en) 1971-11-16

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Application Number Title Priority Date Filing Date
US63071A Expired - Lifetime US3620647A (en) 1969-09-19 1970-08-12 Fuel injection system for internal combustion engines
US63215A Expired - Lifetime US3620648A (en) 1969-09-19 1970-08-12 Fuel injection system for internal combustion engines

Family Applications After (1)

Application Number Title Priority Date Filing Date
US63215A Expired - Lifetime US3620648A (en) 1969-09-19 1970-08-12 Fuel injection system for internal combustion engines

Country Status (5)

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US (2) US3620647A (de)
AT (2) AT301952B (de)
DE (2) DE1947529C3 (de)
FR (2) FR2061388A5 (de)
GB (1) GB1308810A (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4062336A (en) * 1975-05-19 1977-12-13 Cummins Engine Company, Inc. Fuel control valve
US4387686A (en) * 1981-01-27 1983-06-14 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
US4398518A (en) * 1980-01-12 1983-08-16 Robert-Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
US4398519A (en) * 1980-07-02 1983-08-16 Robert-Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
US4593668A (en) * 1984-09-23 1986-06-10 Diesel Kiki Co., Ltd. Injection rate controller for fuel injection pump

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2503346C2 (de) * 1975-01-28 1986-04-03 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffverteilereinspritzpumpe für Brennkraftmaschinen
DE2649893A1 (de) * 1976-10-29 1978-05-11 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
JPS53117126A (en) * 1977-03-22 1978-10-13 Diesel Kiki Co Ltd Fuel regulation device of stright line fuel injection pump
US4271808A (en) * 1978-01-20 1981-06-09 Diesel Kiki Co., Ltd. Fuel injection pump for internal combustion engines
DE19618707C2 (de) * 1996-05-09 1998-12-17 Siemens Ag Verfahren und Vorrichtung zur Regelung eines Kraftstoffvolumenstromes
US6450778B1 (en) * 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
JP5501272B2 (ja) * 2011-03-08 2014-05-21 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB968513A (en) * 1960-11-07 1964-09-02 Expl Des Procedes Chimiques Et Improvements in self-regulating reciprocating pumps, in particular for the injectionof fuel into internal combustion engines
US3320893A (en) * 1965-05-14 1967-05-23 Bosch Gmbh Robert Regulated injection pump
US3403629A (en) * 1966-07-19 1968-10-01 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB968513A (en) * 1960-11-07 1964-09-02 Expl Des Procedes Chimiques Et Improvements in self-regulating reciprocating pumps, in particular for the injectionof fuel into internal combustion engines
US3320893A (en) * 1965-05-14 1967-05-23 Bosch Gmbh Robert Regulated injection pump
US3403629A (en) * 1966-07-19 1968-10-01 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4062336A (en) * 1975-05-19 1977-12-13 Cummins Engine Company, Inc. Fuel control valve
US4398518A (en) * 1980-01-12 1983-08-16 Robert-Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
US4398519A (en) * 1980-07-02 1983-08-16 Robert-Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
US4387686A (en) * 1981-01-27 1983-06-14 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
US4593668A (en) * 1984-09-23 1986-06-10 Diesel Kiki Co., Ltd. Injection rate controller for fuel injection pump

Also Published As

Publication number Publication date
DE1947529C3 (de) 1979-06-13
AT301952B (de) 1972-09-25
DE1947529A1 (de) 1971-04-01
FR2061388A5 (de) 1971-06-18
FR2061460A5 (de) 1971-06-18
US3620648A (en) 1971-11-16
AT301953B (de) 1972-09-25
DE1947528C3 (de) 1975-03-06
DE1947529B2 (de) 1978-10-05
GB1308810A (en) 1973-03-07
DE1947528B2 (de) 1974-07-18
DE1947528A1 (de) 1971-04-01

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