US3631743A - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

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Publication number
US3631743A
US3631743A US29114A US3631743DA US3631743A US 3631743 A US3631743 A US 3631743A US 29114 A US29114 A US 29114A US 3631743D A US3631743D A US 3631743DA US 3631743 A US3631743 A US 3631743A
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US
United States
Prior art keywords
cylinder
control plug
flow passage
regulator
passage section
Prior art date
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
US29114A
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English (en)
Inventor
Konrad Eckert
Franz Eheim
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
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Publication of US3631743A publication Critical patent/US3631743A/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • 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

  • control of the internal combustion engine is effected by throttling to a greater or less'er'extent a regulator fluid displaced by a regulator shuttle, there are provided means to vary the largest possible flow passage section for said regulator fluid, in response to shifting gears in said engine, for varying the maximum r.ptm. thereof.
  • This invention relates to a fuel injection pump for internal combustion engines and is of the type wherein the injected fuel quantities may be varied as a function of the r.p.m. by interrupting the delivery of fuel during the pressure strokes of the piston at least upon reaching a maximum r.p.m. Said interruption is effected during the pressure stroke of the pump piston by opening a bypass channel by means of a reciprocating regulator member which is displaced forwardly by a fluid driven by an auxiliary pump operating synchronously with the main pump.
  • the regulator member is braked during its return motion by directing at least one part of the liquid that has caused its forward motion, through at least one arbitrarily variable throttle, so that for a given flow passage section and upon reaching a predetermined r.p.m. the regulator member, by virtue of the appearance of the so-called fluid abutment," does not return into its original position.
  • the maximum possible flow passage section of the aforenoted throttle determines the maximum r.p.m.
  • the largest flow passage section determining the maximum r.p.m. during normal operation is changeable, preferably as a function of the gear setting, for varying the maximum possible engine r.p.m.
  • FIG. 1 is a schematic sectional view of a first embodiment of the invention
  • FIG. 2 is a sectional view taken along line II-II of FIG. 1;
  • FIG. 3 is a fragmentary schematic sectional view of a second embodiment ofthe invention.
  • FIG. 4 is a plan view of means securing an electromagnet to the pump housing.
  • a pump housing 1 In a pump housing 1 there is provided a cylinder 2 in which operates a pump piston 3. The latter is driven by conventional means, not shown, and is adapted to execute an axial reciprocating motion as well as a rotary motion.
  • a supply conduit 4 Into the cylinder 2 there merge a supply conduit 4 and a determined number of delivery or pressure conduits 5; each of the latter contains a check valve 6.
  • the latter In order to establish connection between the pump work chamber and one of the delivery conduits 5 during each pressure stroke of the piston 3, the latter is provided with a longitudinal distributor groove 7.
  • the suction chamber A is supplied with fuel from a tank B by means of a delivery pump C.
  • a regulator shuttle 12 For the regulation of the fuel quantity delivered through a pressure conduit 5 of the fuel injection pump during each pressure stroke of pump piston 3, there is provided a regulator shuttle 12 which has two snugly fitting terminal heads 12a and 12b and which operates in a cylinder 13.
  • the regulator shuttle 12 controls a bypass channel formed of two bypass channel portions 14a and 14b.
  • Bypass channel portion 14a connects the pump work chamber 2a with that portion of the cylinder 13 which is bounded by heads 12a and 12b.
  • Bypass channel portion 14b in turn, establishes communication between cylinder 13 and suction chamber A, where relatively low pressure prevails.
  • the regulator shuttle 12 is caused to execute forward strokes in response to a periodic force exerted by a regulator fluid which is delivered thereto in a pulsating manner synchronously with the delivery stroke of the pump piston 3. Said fluid is driven by a stepped portion 15 of the piston 3 operating in a cylinder 16. Piston l5 and cylinder 16 thus form an auxiliary pump.
  • the regulator fluid is delivered from cylinder 16 to the terminal face 12c of regulator shuttle 12 through a channel 17 in which there is disposed a check valve 18 preventing fluid flow from the cylinder 13 to cylinder 16 through channel 17.
  • the cylinder 16 is supplied with fuel (regulator fluid) from suction chamber A through a channel 19 opened and closed by the auxiliary piston 15.
  • the portion of the work cylinder 13 adjacent the face of the regulator shuttle I2 is also connected with cylinder 16 by serially arranged channels 20 and 22 communicating with one another through a cylinder 21.
  • Components 20, 21 and 22 form a return channel means.
  • the channel 20 is throttled at 23 by an oblique control edge 25 of a control plug 24.
  • the flow passage section of throttle 23 is varied by angularly displacing plug 24.
  • the regulator fluid driven by the auxiliary pump 15, 16 causes the regulator shuttle 12 to execute its forward strokes against the force of a return spring 26 which tends to maintain the regulator shuttle 12 in, or return the same into, its initial position in engagement with an abutment 27.
  • the regulator shuttle 12 during its return stroke, forces regulator liquid from cylinder 13 through throttle 23 into suction chamber A. In this manner the regulator shuttle 12 is braked during its return stroke. Beyond a predetermined r.p.m. of the piston 3, 15, the regulator shuttle 12, because of its aforenoted retarded return motion, is caused to start a forward motion by the immediately following pressure stroke of the piston prior to its return to its position of rest defined by the abutment 27. This phenomenon is the so-called fluid abutment. As a result of the appearance thereof, the distance necessary for the regulator shuttle 12 to travel for opening the bypass channel 14a, 14b, becomes shorter. This distance continues to decrease as the r.p.m. of piston 3, 15 increases while the flow passage section 23 is maintained at the same value.
  • the control plug 24 is provided with a terminal flange 30 which has a radial opening 31. Axially adjacent the flange 30 there is disposed an electromagnet 32, the armature 33 of which is provided with a pin 34 oriented towards the flange 30.
  • the solenoid 35 is deenergized and the armature 33 assumes its position of rest under the effect of a spring 36, the pin 34 extends into the opening 31 of the flange 30.
  • the armature 33 is prevented from rotating by a pin or abutment 38 which is affixed to the magnetic core 39 and which extends into an opening 37 of armature 33.
  • the throttle 23 may be fully opened by the oblique control edge 25.
  • the electromagnet 32 is deenergized and thus the spring 36 shifts the armature 33 outwardly, the pin 34 extends into the opening 31 of flange 30. In this manner the angle of rotation of control plug 24 is limited.
  • the opening 31 and the course of the control edge 25 are coordinated in such a manner that when pin 34 projects into opening 31 and thus the angular displacement of the control plug 24 is restricted, the maximum flow passage section allowed at 23 by the control edge 25 is substantially smaller than during the energized condition of the electromagnet 32. As a result, the maximum engine r.p.m. is also substantially smaller.
  • the force of the coupling spring 42 is so designed that during normal operation it establishes a clearance-free connection between the setting member 41 and the control plug 24.
  • the spring 42 is disposed about a hollow portion 43 of the setting member 41 and engages with one end a bore 44 of a lug integral with the setting member 41.
  • the other end of spring 42 extends into a bore 45 of a terminal flange 46 integral with the control plug 24.
  • the setting member 41 is rotatably held in a bore of the housing 1 and on a stub 47 which forms part of the control plug 24 and which extends into the hollow portion 43 of the setting member 41.
  • the second embodiment depicted therein comprises a control plug 24' provided with an axial bore 48 in which there is slidably held a setting piston 49.
  • the fuel forced through the conduit 22 by the regulator shuttle 12 is admitted to the conduit 20 through an annular groove 50, one boundary of which is formed as an oblique control edge 25 a radial port 51, an annular circumferential groove 52 provided in the setting piston 49, a radial bore 53, and an annular groove 54.
  • the annular grooves 50 and 54, as well as the radial ports 51 and 53, are provided in the cylindrical wall of the control plug 24'.
  • the control edge 25' throttles to a greater or lesser extent the passage 23' through which the conduit 22 opens into the cylinder 21.
  • the setting piston 49 is fixedly connected with the armature 33 of the electromagnet 32. This arrangement is so designed that when the electromagnet is energized, the setting piston 49 is axially displaced against the force of spring 36 and the flow passage section 59 of the radial port 53 is fully opened. Such a position corresponds to the normal operating conditions.
  • the setting piston 49 is provided with an integral terminal flange 56 having a radial cutout 57 into which extends a pin 58 fixedly secured to the magnet core 39. In this manner the setting piston 49 is prevented from angular displacement.
  • the deenergization of the solenoid 35 occurs when the tractor engine is put into a gear corresponding to the highest tractor speed.
  • the r.p.m. of the engine and thereby the highest tractor speed may be decreased to comply with the legal speed limits.
  • the largest possible flow passage section 23, 59 which determines the maximum r.p.m. and which becomes effective when the electromagnet 32 is deenergized, may be preset in both embodiments by turning the entire electromagnet 32 in the pump housing 1.
  • the electromagnet may be rotated upon temporarily loosening the tightening screws 62.
  • the position of the pin 34 varies with respect to the opening 31, whereas in the second embodiment, the position of the oblique control edge 55 varies with respect to the radial port 53.
  • pressure conduit means communicating with said pump work chamber to carry fuel pressurized in said pump work chamber by each pressure stroke of said pump piston
  • G means to operate said auxiliary piston synchronously with said pump piston
  • a regulator shuttle slidably disposed in said third cylinder and having a work face
  • check valve means disposed in said channel for permitting the flow of liquid therein from said second cylinder to said third cylinder and preventing the flow of liquid therein from said third cylinder to said second cylinder,
  • return channel means communicating with said third cylinder adjacent the work face of said regulator shuttle for carrying the liquid displaced by said work face of said regulator shuttle during the return strokes thereof,
  • throttle means disposed in said return channel means to brake the flow of liquid therein for reducing the speed of said regulator shuttle during its return strokes and for generating, beyond a predetermined speed of said pump piston and said auxiliary piston, a fluid abutment in said third cylinder adjacent said work face, said fluid abutment preventing said regulator shuttle from returning to its initial position of rest, said throttle means including 1. control plug means in a unitary structure having control edge means cooperating with said return channel means to determine the fiow passage section thereof,
  • said electromagnetic means includes an abutment adapted to assume a first position and a second position; when in said first position, said abutment is spaced from the path of motion of said control plug means permitting the latter to vary said flow passage section in response to said arbitrarily operable means, up to a first maximum value; when in said second position, said abutment is in the path of motion of said control plug means permitting the latter to vary said flow passage section in response to said arbitrarily operable means, up to a second maximum value which is smaller than said first maximum value.
  • control plug means varies said flow passage section by rotation; said abutment, when in said second position, limits the range of rotation of said control means.
  • control plug means has an integral flange provided with an opening, said abutment is formed of a pin which, in said first position, is withdrawn from said opening and, in said second position, projects thereinto.
  • control plug means includes A. a rotatable control plug connected to said arbitrarily operable means and having 1. an axial bore,

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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)
  • High-Pressure Fuel Injection Pump Control (AREA)
US29114A 1969-05-02 1970-04-16 Fuel injection pump for internal combustion engines Expired - Lifetime US3631743A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691922383 DE1922383A1 (de) 1969-05-02 1969-05-02 Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
US3631743A true US3631743A (en) 1972-01-04

Family

ID=5733033

Family Applications (1)

Application Number Title Priority Date Filing Date
US29114A Expired - Lifetime US3631743A (en) 1969-05-02 1970-04-16 Fuel injection pump for internal combustion engines

Country Status (5)

Country Link
US (1) US3631743A (enrdf_load_stackoverflow)
AT (1) AT298160B (enrdf_load_stackoverflow)
DE (1) DE1922383A1 (enrdf_load_stackoverflow)
FR (1) FR2047257A5 (enrdf_load_stackoverflow)
GB (1) GB1305775A (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3927654A (en) * 1973-08-22 1975-12-23 Cummins Engine Co Inc Fuel supply system
US4164921A (en) * 1976-10-29 1979-08-21 Robert Bosch Gmbh Fuel injection pump
US4211203A (en) * 1977-12-29 1980-07-08 Diesel Kiki Co., Ltd. Fuel injection pump
US4271805A (en) * 1977-12-29 1981-06-09 Diesel Kiki Co., Ltd. Fuel injection pump

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3209613A (en) * 1961-09-21 1965-10-05 Cav Ltd Hydraulic governors
US3403629A (en) * 1966-07-19 1968-10-01 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3209613A (en) * 1961-09-21 1965-10-05 Cav Ltd Hydraulic governors
US3403629A (en) * 1966-07-19 1968-10-01 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3927654A (en) * 1973-08-22 1975-12-23 Cummins Engine Co Inc Fuel supply system
US4164921A (en) * 1976-10-29 1979-08-21 Robert Bosch Gmbh Fuel injection pump
US4211203A (en) * 1977-12-29 1980-07-08 Diesel Kiki Co., Ltd. Fuel injection pump
US4271805A (en) * 1977-12-29 1981-06-09 Diesel Kiki Co., Ltd. Fuel injection pump

Also Published As

Publication number Publication date
FR2047257A5 (enrdf_load_stackoverflow) 1971-03-12
AT298160B (de) 1972-04-25
GB1305775A (enrdf_load_stackoverflow) 1973-02-07
DE1922383A1 (de) 1970-11-19

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