US3620648A - Fuel injection system for internal combustion engines - Google Patents

Fuel injection system for internal combustion engines Download PDF

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Publication number
US3620648A
US3620648A US63215A US3620648DA US3620648A US 3620648 A US3620648 A US 3620648A US 63215 A US63215 A US 63215A US 3620648D A US3620648D A US 3620648DA US 3620648 A US3620648 A US 3620648A
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US
United States
Prior art keywords
control member
bypass
pump
piston
fuel injection
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
US63215A
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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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Publication of US3620648A publication Critical patent/US3620648A/en
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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
    • 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 control member during its return stroke, drives the fluid through a controllable throttle channel to create a fluid abutment, i.e., it does not return to the initial position.
  • a second bypass is provided subject to control by the control member as well as by a slide valve; also synchronous with the main pump, the characteristic feature being the coordination of the control member with the slide valve in dependence on the variable position of the fluid abutment and a throttling restriction provided in the second bypass.
  • 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 is variable in dependence on the rpm. 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 r.p.m.
  • 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 system of this type is known from German Pat. No. 1,286,804.
  • the second bypass is blocked by the control member during the starting of the engine, and, furthermore, as long as the control member returns to its initial position (no fluid abutment) or the fluid abutment is below a predetermined level, it is opened by the injection pump piston before the control member opens the first bypass.
  • means are provided for preventing within the full load range of r.p.m.
  • combustion noise particularly in the low load range of rpm. and in the idling state. This is caused, apart from thermal conditions, by the relatively low duration of the injection process corresponding to the small amount of fuel to be injected under these conditions. It is possible to substantially reduce this combustion noise by extending the duration of the injection process, for instance, by extending the effective period of supply for each pressure stroke of the injection pump.
  • the duration of the supply interval is extended by means of a calibrated throttle passage connecting the injection pump work chamber in the idling state and in the state of partial loading with a low-pressure space, whereby the amount of fuel supplied by the injection pump is divided into two partial flows, only one of which is injected.
  • the switching off of the second partial flow under partial load conditions then takes place with a smooth transition.
  • the throttle area is controllable.
  • the slide valve may be the piston of the main injection pump or that of the auxiliary pump, as is known per se.
  • bypass control member in which the bypass control member is provided with a peripheral notch and a longitudinal notch connecting therewith, an end surface may be provided for delimiting the longitudinal notch in the axial direction and controlling the second bypass throttling restriction being provided in the longitudinal notch.
  • FIG. 1 is a longitudinal section through the fuel injection system.
  • FIG. 2 is a modified form of the control member with the throttle area thereof shown in partial longitudinal section.
  • FIG. 3 shows the control member of FIG. 2 in cross section taken on line Ill-III of FIG. 2.
  • FIG. 4 shows diagrams illustrating the rate of fuel supply, the stroke of the control member and that of the injection pump piston as functions of the angular position of a cam driving the system.
  • FIG. 1 there is shown a housing 1 of a fuel injection pump having a combined slide valve and piston 2 operating in a cylinder 3 and delimiting therewith a work chamber 4.
  • Piston 2 is reciprocated by means not shown, as illustrated by the arrows in FIG. 1, and simultaneously therewith rotates about its axis.
  • fuel is supplied to work chamber 4 from a suction chamber 5 via suction borings 6 and one of a plurality of Iongitudinal notches 7 on the piston, an annular notch 8, and an axial bore 9, which connects with notch 8 through a transversal bore 10 and which ends in work chamber 4.
  • piston 2 delivers fuel sequentially to supply conduits 12, in each of which there is provided a nonretum valve 13 with a release piston 13, and which are connected to fuel pressure lines, not shown, leading to the different injection valves of the engine.
  • Nonreturn and release valve 13 in a manner known per se, prevents a delayed spurious injection from taking place after the termination of the actual injection process owing to pressure variation and elasticity in the fuel pressure line as well as the compressibility of the fuel.
  • Longitudinal notches 7, only two of which are shown, and supply conduits 12, of which only one is shown, are spaced uniformly around the circumference of piston 2 and of cylinder 3 in a number corresponding to the number of cylinders of the engine to be supplied with fuel from the pump. Whereas suction bore 6 and supply conduit 12 are in the same plane, distributing notch 11 and notches 7 are staggered, since notch 11 opens up one of the supply conduits when the longitudinal notches 7 are disconnected from suction bore 6 and vice versa.
  • Control member 14 operates in a cylinder 15 and controls the connection between one section 160 of a bypass channel leading from work chamber 4 to cylinder 15 and the other section 16b leading from cylinder 15 to suction chamber 5.
  • Control member 14 has an annular notch 17, which is in continuous connection with channel section 16a and is disconnected from section 16b in the inoperative position shown in FIG. 1.
  • a section of the main pump piston system is of larger diameter and forms the piston 18 of an auxiliary pump operating in a cylinder 19.
  • the liquid displaced by piston 18 actuates control 'member 14 during its pressure stroke.
  • Connecting with the end surface area of piston 18 are longitudinal notches 20 provided on the cylindrical surface thereof in a number corresponding to that of notches 7 and in the same planes as the latter.
  • Suction borings 21 are provided to cooperate with notches 20 and during the suction stroke of piston 18 fuel flows from suction chamber 5 into the work chamber of auxiliary pump 18, 19.
  • Piston 18 during the subsequent pressure stroke displaces fuel substantially via notches 20 and a channel 22 into cylinder 15 in front of control member 14.
  • Channel 22 and suction borings 21 are staggered relative to each other.
  • control member 14 As control member 14 is displaced from its inoperative position by auxiliary pump 18, 19, it establishes a connection between channel sections 16a and 16b shortly before the end of its operative stroke.
  • the inoperative position is determined by fixed stop 23 provided in cylinder 15 under the piston.
  • control member 14 is driven by a return spring 24 and displaces at least a portion of the liquid which caused the operating stroke thereof back via a channel 25 into cylinder 19 of the auxiliary pump, channel 22 being then closed by a nonretum valve 26.
  • Channel 25 has interposed therein a cylinder 27, in which a slide valve 28 is axially adjustable by means of a screw 29.
  • slide valve 28 Provided on slide valve 28 is an annular notch 30, with which the section of channel 25 leading from cylinder 15 connects freely, whereas the section of channel 25 connecting with cylinder 19 can be throttled by slide valve 28 at the point 31 where it ends in cylinder 27.
  • control member 14 The return stroke of control member 14 is decelerated to a greater or lesser extent depending upon the cross-sectional area of the throttle aperture 31. Above a value of r.p.m. determined by aperture 31, the pressure stroke of auxiliary pump 18, 19 sets in before control member 14 could return to its initial position. This represents a fluid abutment" for control member 14, owing to which it will start its forward stroke from another initial position, whereby channel sections 16a and 16b are interconnected at an earlier time. This leads to a decrease in the amount of fuel supplied and therefore also in the r.p.m. of the engine supplied from the injection system.
  • the forward stroke of control member 14 in any case terminates when the lower edge thereof opens up a safety bore 32 connecting with suction chamber 5 and through which the remainder of the fuel supplied from auxiliary pump 18, 19 is drained off.
  • control member 14 Before control member 14 opens up bypass channel 16b, it opens a second bypass channel 33, which also connects with suction chamber 5.
  • Channel 33 is interrupted by cylinder 3, in which piston 2 operates.
  • annular notch 34 For the control of channel 33 there is provided on the cylindrical surface of piston 2 an annular notch 34, through which the second bypass is held open as long as piston 2 is in its lower inoperative position, whereas it is closed after the pump piston has performed a certain fraction of its pressure stroke. This fraction of the stroke which is required to be performed by piston 2 in order to close bypass channel 33 is selected in such a manner that at full load, i.e. as long as control member 14 returns to stop 23, channel 33 is closed by piston 2 before the control member 14 opens channel 33.
  • channel 33 is opened by the control member 14 before piston 2 has performed the said fraction of its stroke. Therefore, a portion of the fuel delivered by piston 2 will flow via channel section 16a, annular notch 17 and second bypass 33 into suction chamber 5 until the second bypass is blocked by piston 2.
  • throttling restriction 35 which can be adjusted at will with the aid of an adjustment screw 36.
  • FIGS. 2 and 3 illustrate a modified forrn 14a of the control member, in which a restriction 35a is provided between member and cylinder 15.
  • a restriction 35a is provided between member and cylinder 15.
  • Notch 37 controls channel 33 and is provided close to its end at notch 17 with a throttling restriction 35a.
  • the top diagram shows the amount of q of fuel supplied, the middle diagram the portion S, of its stroke performed by control member 14, and the bottom diagram the portions S, of its stroke performed by piston system 2, 18 as functions of the angle of rotation a of a driving means, such as a cam, causing the reciprocation of piston system 2, 18.
  • a driving means such as a cam
  • the top diagram shows three graphs (Vl, Vii, VIII) of the amount of fuel supplied, the middle diagram shows four characteristics (1, 11, ill, IV) for the path 8, of the control member and the bottom diagram is a graph V illustrating the sinusoidal movement of piston 2, 18, i.e. the path S thereof.
  • the horizontal line S of the middle diagram shows the portion of the stroke that has to be performed by control member 14 from fixed stop 23 before second bypass channel 33 is opened (intersection of line S with characteristics 1 to ill).
  • Horizontal line S shows the portion of the stroke of the control member from fixed stop 23 which is required for section 161: of the first bypass to be opened (intersections of line 5,, with characteristics 1 to 1V).
  • Characteristic 1 shows the movement performed by control member 14 as long as it is able to return to stop 23.
  • Characteristics II to IV in dash lines, dot-dash and full lines, respective) show the movement of control member 14 for difierent increasing levels of the fluid abutment designated 5,, S, and 5,, respectively.
  • the horizontal line 8, of the lower diagram shows the position of piston system 2, 18 in which suction borings 6 and 21 are closed by pistons 2 and 18, respectively, and the forward stroke of control member 14 begins. This occurs at the angular position a At angular position a when piston system 2, 18 has performed the portion 8,, of its stroke, annular notch 34 is disconnected from the second bypass channel 33, which is then blocked.
  • characteristic Vl illustrates the amount of fuel supplied by injection pump piston 2 in the entire range of full load r.p.m.a.
  • a fluid abutment for instance at the level 5: corresponding to position a: (middle diagram), as represented by dash-line characteristic II, the second bypass is opened up by control member 14 at angular position a, (intersection a S whereby, if restriction 35 is fully open, the fuel displaced by piston 2 is diverted into suction chamber 5.
  • any position a (horizontal sections shown in upper diagram) vary according to the r.p.m. owing to the increase in throttling effect with the increasing r.p.m., i.e. decreasing duration of the flow, so that from a certain high value of r.p.m. on, the throttling effect of restriction 35 is large enough to cause the inclination of graphs VII and VIII within this range to be approximately as large as that of curve VI. If the restriction 35 were closed completely, graphs VII or VIII would coincide with graph VI; however, they would end at the intersection with the ordinate a, or 0 respectively.
  • 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
  • an auxiliary pump for operation in synchronism with said injection pump and supplying pressure liquid to said control member during the pressure stroke thereof means for exerting a return force on said control member
  • 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
  • said second bypass (33) is opened up by said control member (14) before said first b ass (16), said second bypass (33) in the absence of a fluid abutment being closed by said slide valve (2) before being opened by said control member (14) and in the presence of said fluid abutment being opened by said control member (14) for increasing levels of said fluid abutment at an increasingly earlier time relative to the earlier closing thereof by said slide valve (2), a throttling restriction (35) being provided in said second bypass 33).
  • a fuel injection system in which there are provided on said control member (14) for controlling said bypasses (16, 33) an annular notch (17), a longitudinal notch (37) connecting therewith and an end surface delimiting said longitudinal notch (37) in the axial direction for controlling said second bypass (33), said longitudinal notch (37) having a throttling restriction 35a.

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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)
US63215A 1969-09-19 1970-08-12 Fuel injection system for internal combustion engines Expired - Lifetime US3620648A (en)

Applications Claiming Priority (2)

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

Publications (1)

Publication Number Publication Date
US3620648A true US3620648A (en) 1971-11-16

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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
US63071A Expired - Lifetime US3620647A (en) 1969-09-19 1970-08-12 Fuel injection system for internal combustion engines

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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

Country Status (5)

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US (2) US3620648A (enExample)
AT (2) AT301952B (enExample)
DE (2) DE1947528C3 (enExample)
FR (2) FR2061388A5 (enExample)
GB (1) GB1308810A (enExample)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4164921A (en) * 1976-10-29 1979-08-21 Robert Bosch Gmbh Fuel injection pump
US4200075A (en) * 1977-03-22 1980-04-29 Diesel Kiki Company, Ltd. Fuel injection apparatus
US4271808A (en) * 1978-01-20 1981-06-09 Diesel Kiki Co., Ltd. Fuel injection pump for internal combustion engines
US5971718A (en) * 1996-05-09 1999-10-26 Siemens Aktiengesellschaft Method and apparatus for regulating a volumetric fuel flow between a feed pump and a high-pressure pump
US20040076530A1 (en) * 2000-12-07 2004-04-22 Spoolstra Gregg R. Pump system with high pressure restriction
US20120227711A1 (en) * 2011-03-08 2012-09-13 Hitachi Automotive Systems, Ltd. High-Pressure Fuel Supply Pump

Families Citing this family (6)

* 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
US4062336A (en) * 1975-05-19 1977-12-13 Cummins Engine Company, Inc. Fuel control valve
DE3000977A1 (de) * 1980-01-12 1981-07-23 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen, insbesondere fuer dieselmotoren
DE3024963A1 (de) * 1980-07-02 1982-01-28 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen, insbesondere fuer dieselmotoren
US4387686A (en) * 1981-01-27 1983-06-14 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
JPS6176727A (ja) * 1984-09-23 1986-04-19 Diesel Kiki Co Ltd 燃料噴射ポンプの噴射率制御装置

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 (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4164921A (en) * 1976-10-29 1979-08-21 Robert Bosch Gmbh Fuel injection pump
US4200075A (en) * 1977-03-22 1980-04-29 Diesel Kiki Company, Ltd. Fuel injection apparatus
US4271808A (en) * 1978-01-20 1981-06-09 Diesel Kiki Co., Ltd. Fuel injection pump for internal combustion engines
US4327696A (en) * 1978-01-20 1982-05-04 Diesel Kiki Co., Ltd. Fuel injection pump for internal combustion engines
US5971718A (en) * 1996-05-09 1999-10-26 Siemens Aktiengesellschaft Method and apparatus for regulating a volumetric fuel flow between a feed pump and a high-pressure pump
US20040076530A1 (en) * 2000-12-07 2004-04-22 Spoolstra Gregg R. Pump system with high pressure restriction
US6854962B2 (en) * 2000-12-07 2005-02-15 Robert Bosch Gmbh Pump system with high pressure restriction
US20120227711A1 (en) * 2011-03-08 2012-09-13 Hitachi Automotive Systems, Ltd. High-Pressure Fuel Supply Pump
US9828958B2 (en) * 2011-03-08 2017-11-28 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump
US10788004B2 (en) 2011-03-08 2020-09-29 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump

Also Published As

Publication number Publication date
DE1947529B2 (de) 1978-10-05
DE1947529A1 (de) 1971-04-01
FR2061460A5 (enExample) 1971-06-18
AT301952B (de) 1972-09-25
DE1947528B2 (de) 1974-07-18
US3620647A (en) 1971-11-16
DE1947529C3 (de) 1979-06-13
DE1947528C3 (de) 1975-03-06
FR2061388A5 (enExample) 1971-06-18
GB1308810A (en) 1973-03-07
DE1947528A1 (de) 1971-04-01
AT301953B (de) 1972-09-25

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