US3628892A - Fuel injection pump for internal-combustion engines - Google Patents

Fuel injection pump for internal-combustion engines Download PDF

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Publication number
US3628892A
US3628892A US10887A US3628892DA US3628892A US 3628892 A US3628892 A US 3628892A US 10887 A US10887 A US 10887A US 3628892D A US3628892D A US 3628892DA US 3628892 A US3628892 A US 3628892A
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United States
Prior art keywords
fuel
arbitrarily
control plunger
expandable member
heat expandable
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Expired - Lifetime
Application number
US10887A
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English (en)
Inventor
Franz Eheim
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Robert Bosch GmbH
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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

Definitions

  • Greigg 54 FUEL INJECTION PUMP FOR INTERNAL- ABSTRACT In a fuel injection pump in which the fuel quantil COMBUSTION ENGINES tles delivered thereby to an internal-combustion engine are 5 Claims, 2 Drawin Figs.
  • t ere is associate wit sai p ungcr a [52] U.S.Cl 4411770229921; heat expandable P which independently of the arbitrary 5] l t Cl F04) 49/00 setting of said plunger, causes a displacement of the plunger in 417/292 response to the changes in the temperature of the liquid l ie 0 .593 137/468, p g through Said throttle in order to compensate for the temperature-dependent changes in the viscosity of said liquid.
  • This invention relates to a fuel injection pump for internalcombustion engines and is of the type wherein the fuel quantity to be delivered to the engine is affected by an arbitrarily displaceable control plunger which, by means of a control edge, varies a throttle determining the flow rate of a liquid.
  • the fuel quantities to be injected are determined by opening a bypass channel of the pump work chamber by means of a regular shuttle.
  • the latter is caused to execute its forward strokes by a regulating liquid driven by an auxiliary pump which operates synchronously with the main fuel pump.
  • the regulator shuttle is braked by directing at least one part of the regulating liquid that caused its preceding forward stroke through the aforenamed variable throttle.
  • the regulator shuttle due to the appearance of a so-called fluid abutment, does no longer return into its original position of rest. In such a case, the forward strokes of the regulator shuttle start from an advanced position of rest. As a result, the bypass channel of the pump work chamber is opened at an earlier moment and consequently, the delivered fuel quantities are decreased.
  • the magnitude of the flow rate through any given flow passage section of the throttle depends upon the viscosity of the liquid. As long as the regulating liquid is relatively cold and thus of relatively high viscosity (for example, during starting of a cold internal-combustion engine), the fluid abutment increases rapidly in case of a flow passage section set for idling. Consequently, the fuel quantities to be injected drop sharply. This is disadvantageous because the cold engine, due to the higher hysteresis, needs a greater quantity of fuel.
  • the throttle control means is formed of a first part which is arbitrarily adjustable, a second part which is a plunger that includes a control edge and a third part which is a heat expandable member causing relative displacements between the first and second parts as the temperature of the liquid passing through the throttle changes.
  • a temperature-responsive change in the flow passage section of the throttle is obtained.
  • the aforenoted adjustment of the engine r.p.m. is also advantageous in the maximum r.p.m. range to eliminate substantial fluctuations.
  • FIG. I in an axial diagrammatic sectional view of a fuel injection pump including it throttle control means forming the first embodiment of the invention.
  • FIG. 2 is an isometric view of a throttle control means according to a second embodiment of the invention.
  • a pump housing 1 is provided with a bore 2 in which operates a main pump piston 3 driven by a mechanism (not shown) in such a manner that it executes an axial reciprocating motion as well as a rotary motion.
  • a mechanism not shown
  • bore 2 there merge an inlet channel 4 and a certain number of output or delivery channels 5, each of the latter containing a check valve 6.
  • a longitudinal distributor groove 7 on the outer face of the piston 3.
  • the latter is connected with the supply channel 4 through an axial channel 8 which, on the one hand, merges in the pump work chamber 20 and, on the other hand, terminates in a transversal channel 9 which establishes communication with the supply channel 4 through an annular groove 10 and axially extending grooves 1 1.
  • a regulator shuttle 12 which operates in a cylinder 13 and which controls a bypass channel formed of two channel portions 14a and 14b.
  • the bypass channel portion 14a connects the pump work chamber 2a with the cylinder 13, while the bypass channel portion 14!: connects the cylinder 13 with a chamber of lower pressure.
  • a regulating liquid which is delivered in a pulsating manner synchronously with the pressure strokes of the main pump piston 3.
  • the regulating liquid is driven by means of an auxiliary piston 15 which is formed as a stepped portion of piston 3 and which operates in a cylinder 16. From the latter there extends a delivery conduit 17 through a check valve 18 to the lower end portion of the cylinder 13.
  • a supply conduit 19 merges in the cylinder 16 and is controlled by the auxiliary piston 15.
  • the cylinder 16 communicates with the lower end portion of the cylinder 13 by means of a channel 20 which leads from cylinder 16 to a cylinder 21 and by means of a channel 22 extending from cylinder 21 to cylinder 13.
  • the opening through which the channel 20 merges into the cylinder 21 is throttled at 23.
  • the free flow passage section of throttle 23 may be varied by the control edge 24a of a control plunger 24, the axial position of which may be set by means of a screw 25.
  • a pin 34 which may be connected with a mechanism (not shown) for the arbitrary actuation of screw 25.
  • the regulating liquid delivered by the auxiliary pump 15, 16 causes a forward stroke of the regulator shuttle 12 against the force of a return spring 26 which tends to maintain the regulator shuttle 12 in its position of rest determined by an abutment 27.
  • the forward stroke of the regulator shuttle 12 is terminated at the moment when its lower control edge 12a opens a bypass channel 28.
  • the regulator shuttle l2 establishes communication between the two bypass channel portions 14a and 14b by means of the control edge 12b, the fuel delivery from the pump work chamber 2a through the delivery channel 5 is interrupted, since the fuel, during the remainder of the pressure stroke of piston 3, is driven thereby through the bypass channel 14a, 14b.
  • the return stroke of the regulator shuttle 12 is braked by the regulating liquid which is displaced from the cylinder 13 through the throttle 23 by the returning regulator shuttle 12. Beyond a determined operational speed of the pistons 3 and 15. the regulator shuttle 12, due to the aforenoted braking effect, will be forced by the regulating liquid to execute the next forward stroke before returning to its initial position of rest determined by the abutment 27. This phenomenon is the socalled fluid abutment, by virtue of which the stroke of the regulator shuttle l2 necessary for establishing communication between the bypass channel portions 14a and 14b becomes shorter. It will be understood that the more the operating speed of the pistons 3 and 15 increases for the same flow passage section of throttle 23, the shorter will be the aforenoted stroke of the regulator shuttle 12.
  • the r.p.m. of the engine is determined by the setting screw 25. To each position of screw 25 and thus to each flow passage section of throttle 23, there corresponds a certain rpm.
  • the regulating fluid is more viscous in a cold condition than at normal temperatures so that in case of a cold regulating liquid because of the more viscous and thus smaller fuel quantities flowing through the throttle 23 during each return stroke of the regulator shuttle 12, the fluid abutment rises more rapidly and the fuel injection pump cuts off earlier. in case of a cold engine such occurrence leads to stalling.
  • a heat expandable member 30 which may be made of a synthetic material or metal (bimetallic element) expands in response to warmer temperatures and contracts at colder temperatures.
  • a heat expandable member 30 expands in response to warmer temperatures and contracts at colder temperatures.
  • Such changes in the dimension of the heat expandable part 30 cause an axial shift of the control plunger 24 varying the flow passage section of throttle 23. In this manner it is achieved that for a given setting of screw 25, the flow passage section 23 is smaller at higher temperatures than at lower temperatures.
  • FIG. 2 there is shown a second embodiment of the throttle control means associated with throttle 23.
  • This throttle control means comprises a control plunger 24' and a setting screw 25 having a first head segment 31 integral therewith.
  • a second head segment 32 is held concentrically and coplanar with the first head segment 31 and is rotatable relative thereto.
  • a heat expandable member 33 also having a segmentlike configuration. As the segment 33 expands or contracts in response to temperature changes of the regulating liquid, the head segments 31 and 32 are displaced angularly with respect to one another. As a result, the control plunger 24' is dis placed varying the flow passage section of throttle 23.
  • control plunger is integral with a threaded portion or screw to be axially displaced by rotation and with a segment head; said arbitrarily settable part is formed as a segment member arranged adjacent and rotatable with respect to said segment head, said heat expandable member has a segment configuration and is inserted between said segment head and said segment member, the changes in dimension of said heat expandable member effect an axial displacement of said control plunger by rotation with respect to said arbitrarily settable part.
  • a fuel injection pump associated with an internal-combustion engine comprising A. a main piston delivering fuel, during its pressure strokes,
  • a regulator shuttle executing alternating forward strokes and return strokes, said regulator shuttle opening said bypass channel during said forward strokes to interrupt delivery of fuel from said pump work chamber to said engine during one part of each pressure stroke of said main piston,

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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)
US10887A 1969-02-28 1970-02-12 Fuel injection pump for internal-combustion engines Expired - Lifetime US3628892A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691910090 DE1910090A1 (de) 1969-02-28 1969-02-28 Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
US3628892A true US3628892A (en) 1971-12-21

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ID=5726598

Family Applications (1)

Application Number Title Priority Date Filing Date
US10887A Expired - Lifetime US3628892A (en) 1969-02-28 1970-02-12 Fuel injection pump for internal-combustion engines

Country Status (5)

Country Link
US (1) US3628892A (de)
AT (1) AT297406B (de)
DE (1) DE1910090A1 (de)
FR (1) FR2041058B1 (de)
GB (1) GB1300133A (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4222713A (en) * 1979-05-29 1980-09-16 Caterpillar Tractor Co. Temperature responsive fuel compensator
US4278407A (en) * 1978-10-27 1981-07-14 Nissan Motor Company, Ltd. Device for controlling an amount of fuel injection in a diesel engine
US20050238498A1 (en) * 2004-04-23 2005-10-27 Anthony Alves Variable output pump device
US20090178649A1 (en) * 2005-11-23 2009-07-16 Wärtsilä Finland Oy Injection pump for a piston engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3921244A1 (de) * 1989-06-29 1991-01-03 Kloeckner Humboldt Deutz Ag Foerderbeginnversteller fuer den kaltstart von brennkraftmaschinen

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2980173A (en) * 1955-10-24 1961-04-18 Bendix Corp Starting control for gas turbine engines
US3082787A (en) * 1958-06-09 1963-03-26 Vickers Inc Thermal responsive throttle valve
US3096716A (en) * 1960-03-11 1963-07-09 Bosch Arma Corp Control rod for fuel injection pump
US3340893A (en) * 1964-11-20 1967-09-12 Heald Machine Co Throttle

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2980173A (en) * 1955-10-24 1961-04-18 Bendix Corp Starting control for gas turbine engines
US3082787A (en) * 1958-06-09 1963-03-26 Vickers Inc Thermal responsive throttle valve
US3096716A (en) * 1960-03-11 1963-07-09 Bosch Arma Corp Control rod for fuel injection pump
US3340893A (en) * 1964-11-20 1967-09-12 Heald Machine Co Throttle

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4278407A (en) * 1978-10-27 1981-07-14 Nissan Motor Company, Ltd. Device for controlling an amount of fuel injection in a diesel engine
US4222713A (en) * 1979-05-29 1980-09-16 Caterpillar Tractor Co. Temperature responsive fuel compensator
US20050238498A1 (en) * 2004-04-23 2005-10-27 Anthony Alves Variable output pump device
US20090178649A1 (en) * 2005-11-23 2009-07-16 Wärtsilä Finland Oy Injection pump for a piston engine
US7603987B2 (en) * 2005-11-23 2009-10-20 Wartsila Finland Oy Injection pump for a piston engine

Also Published As

Publication number Publication date
DE1910090A1 (de) 1970-11-05
AT297406B (de) 1972-03-27
FR2041058B1 (de) 1976-02-20
GB1300133A (en) 1972-12-20
FR2041058A1 (de) 1971-01-29

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