US3699939A - Fuel injection pump for internal combustion engines and method of fuel control - Google Patents

Fuel injection pump for internal combustion engines and method of fuel control Download PDF

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Publication number
US3699939A
US3699939A US44017A US3699939DA US3699939A US 3699939 A US3699939 A US 3699939A US 44017 A US44017 A US 44017A US 3699939D A US3699939D A US 3699939DA US 3699939 A US3699939 A US 3699939A
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United States
Prior art keywords
bypass channel
pump
valve means
fuel
work chamber
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
US44017A
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English (en)
Inventor
Konrad Eckert
Franz Eheim
Gerald Hofer
Claus Koster
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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 US3699939A publication Critical patent/US3699939A/en
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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

  • This invention relates to a fuel injection pump for internal combustion engines and is of the type which is provided with at least one reciprocating pump piston and with bypass channel means extending from the pump work chamber and including a throttle.
  • An aforenoted prolongation of the injection period is obtained by means of the so-called advance injection methods in which first a small fuel quantity is injected followed by the main fuel quantity.
  • a known fuel injection pump of the aforenoted type such as disclosed in French Pat. No. 1,495,537
  • the bypass channel leads into a hydraulic accumulator, the pressure characteristics of which are variable for altering the course of the injection.
  • Such an arrangement is complex and disadvantageous for high partial load or full load conditions since, even when the accumulator piston is blocked in this rpm range, the structurally necessary enlargement of the detrimental space of the pump work chamber has an adverse effect on the course of the injection.
  • the bypass channel is closed beyond the idling rpm by means of a valve which preferably is actuated in unison with the fuel quantity control member of the fuel injection pump.
  • FIG. 1 is an axial sectional view of a fuel injection pump according to the preferred embodiment
  • FIG. 2 is a view of one part shown in FIG. 1 after a 90 turn and FIG. 3 is a diagram illustrating the function of the flow passage sections F with respect to the angle of rotation at of the fuel quantity control or setting member.
  • the fuel injection pump shown therein comprises a piston l which reciprocates in a cylinder 2, the upper portion of which, together with the radial terminal face of piston 1, defines a pump work chamber 3.
  • the pump piston l which also serves as a distributor, sequentially supplies with fuel the cylinders (not shown) of a multi-cylinder internal combustion enginetalso not shown).
  • the pump piston I is reciprocated and simultaneously rotated as indicated by arrows A by means not shown.
  • the pump work chamber 3 is supplied with fuel from a suction chamber 4 through a control bore 5, one of the longitudinal grooves 6, an annular groove 7, and an axial bore 8 directly communicating with the pump work chamber 3.
  • the axial bore 8 is provided in piston 1 and is connected with the annular groove 7 by means of a transversal bore 9.
  • the pump piston l delivers fuel through a longitudinal distributor groove 10 and through one of pressure channels 11, each of which contains a check valve 12.
  • Each pressure channel 11 extends from the cylinder 2 and is connected with associated pressure conduits, not shown, which, in turn, extend to the individual fuel injection valves (also not shown), mounted in the internal combustion engine.
  • the longitudinal distributor groove 10, the annular groove 7, as well as the longitudinal grooves 6 are provided in the lateral face of the piston 1.
  • the longitudinal distributor groove 10 terminates on the radial face of the piston 3 and thus merges into the pump work chamber 3.
  • the longitudinal grooves 6, of which only two are shown in the drawing, and the pressure or delivery channels 11, of which only one is shown, are arranged uniformly spaced about the circumference of piston l and cylinder 2 and their number equals that of the cylinders of the engine with which the fuel injection pump is associated.
  • the fuel quantity control of the fuel injection pump is effected by means of a regulator shuttle 14 which is disposed between a bypass channel portion 15a merging into the pump work chamber 3 and a bypass channel portion 15b communicating with the suction chamber 4.
  • the regulator shuttle 14 controls the hydraulic communication between the bypass channel portions 15a and 15b. When such communication is established, the delivery of fuel to the engine is interrupted although the pressure stroke of the pump piston is still in progress.
  • bypass channel portions 15a and 15b open into a cylinder 16 in which the regulator shuttle l4 reciprocates.
  • the latter is provided with an annular groove 17 which is in continuous communication with the bypass channel portion 15a, but, as shown in FIG. 1, is separated from the bypass channel portion 15b when the regulator shuttle I4 is in its position of rest determined by an abutting relationship between the pump housing and a flange 23 forming part of the regulator shuttle 14.
  • auxiliary piston 18 operating in a cylinder 19.
  • the liquid displaced by the piston 18 shifts the regulator shuttle 14 in a direction of its forward motion.
  • longitudinal grooves 20 which are disposed on the lateral face of the piston 18 and which equal the number of the longitudinal grooves 6.
  • fuel is admitted from the suction chamber 4 through a control bore 21 and longitudinal grooves 20 into the work chamber of the auxiliary pump 18, 19.
  • the auxiliary piston 18 forces fuel substantially through the channel 22 into the cylinder 16 to affect the adjacent radial face of the regulator shuttle l4.
  • the regulator shuttle 14 when displaced from its position of rest by the fuel forced into cylinder 16 by the piston 18, shortly before the end of its possible path of travel, establishes communication between the bypass channel portions a and 15b. At least one part of the fuel that caused the forward motion of the regulator shuttle 14, is forced by the latter, during its return motion caused by spring 24, through a channel 25 back into the cylinder 19 of the auxiliary pump. During this occurrence the channel 22 is closed by a check valve 26.
  • the channel 25 passes radially through a cylinder bore 27 in which there is disposed a setting member 28 which is axially reciprocable and rotatable as indicated by arrows B. in the lateral face of the latter there is provided a circumferential control groove 29 which has an oblique control edge 36 to vary, during angular displacement of the setting member 28, the flow passage section of a throttle 30 of the channel 25.
  • the diametrically opposite continuation of the channel 25 freely merges into the control groove 29.
  • the return motion of the regulator shuttle 14 is braked to a greater or lesser extent.
  • the auxiliary pump l8, l9 begins a new pressure stroke before the regulator shuttle I4 is able to return to its initial position in which flange 23 abuts the pump housing.
  • the regulator shuttle l4 begins its forward motion from an advanced initial position.
  • the bypass channel portions 150 and 15b are interconnected with one another at an earlier moment during the pressure stroke. in this manner, the injected fuel quantities are decreased and, consequently, the rpm of the internal combustion engine, with which the fuel injection pump is associated, also decreases.
  • a release bore 31 connects the cylinder 16 of the regulator shuttle 14 with the suction chamber 4 and is closed by the lateral face of the regulator shuttle 14 during normal operation.
  • the release bore 31, as a safety means, determines the extreme position which the regulator shuttle 14 may assume during its forward motion subsequent to hydraulically connecting the bypass channels 15a, 15b with one another.
  • the channel 34 passes radially through cylinder 27 and is controlled by the setting member 28.
  • the setting member 28 is provided with a longitudinal groove 35 which has a bounding edge 38 extending parallel to the axis of the setting member 28 and determines, dependent on the angular position of the setting member 28, a flow passage section of throttle 37 of the channel 34 (FIG. 2).
  • the edge 38 of the groove 35 passes over the discharge channel 34 and closes the latter.
  • the control edge 38 is so arranged with respect to the oblique control edge 36 of the groove 29 of the setting member 28 that the bypass channel 34 is closed at the moment when the rpm of the engine exceeds the low load rpm range.
  • this mechanism may be pre-set.
  • a second, adjusted axial position of the setting member 28 is shown in broken lines.
  • a second throttle 39 associated with the bypass channel 34.
  • the flow passage section of the throttle 39 is variable by means of a setting screw 40.
  • a check valve 41 disposed in the bypass channel 34 and having a closing spring, the force of which may be varied by means of an adjusting mechanism 42.
  • the ordinate indicates the free flow passage section F of the throttle 30, while the abscissa indicates the angle of rotation a of the setting member 28.
  • the curves 30' and 30" characterize the function of the flow passage section of throttle 30 in two different axial positions of setting member 28.
  • the curve 37' relates to the flow passage section of the throttle 37.
  • valve means controlling the bypass channel 34 may be actuated electromagnetically or by hydraulic pressure that increases with increasing rpm, or by other suitable means.
  • a fuel injection pump for an internal combustion engine said pump being of the type that includes a pump work chamber and at least one reciprocating pump piston associated with said chamber, the improvement comprising,
  • said movable valve means being in continuous communication with said pump work chamber through said bypass channel at least for the entire duration of each delivery stroke and being in said open position for said entire duration at the idling rpm and
  • An improvement as defined in claim 4 including A. hydraulically operated means for determining the injected fuel quantities by interrupting the injection of fuel during one part of each delivery stroke of said reciprocating pump piston,
  • a fuel injection pump for an internal combustion engine said pump being of the type that includes a pump work chamber and at least one reciprocating main pump piston associated with said chamber, the improvement comprising in combination,
  • valve means disposed in said first bypass channel and continuously communicating with said pump work chamber through said first bypass channel at least for the entire duration of each delivery stroke of said reciprocating main pump piston, said valve means being in an open position for said entire duration at the idling rpm,

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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)
US44017A 1969-06-19 1970-06-08 Fuel injection pump for internal combustion engines and method of fuel control Expired - Lifetime US3699939A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691931039 DE1931039A1 (de) 1969-06-19 1969-06-19 Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
US3699939A true US3699939A (en) 1972-10-24

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ID=5737396

Family Applications (1)

Application Number Title Priority Date Filing Date
US44017A Expired - Lifetime US3699939A (en) 1969-06-19 1970-06-08 Fuel injection pump for internal combustion engines and method of fuel control

Country Status (13)

Country Link
US (1) US3699939A (enrdf_load_html_response)
JP (1) JPS5323449B1 (enrdf_load_html_response)
AT (1) AT299625B (enrdf_load_html_response)
CH (1) CH500377A (enrdf_load_html_response)
DE (1) DE1931039A1 (enrdf_load_html_response)
ES (1) ES380887A1 (enrdf_load_html_response)
FR (1) FR2052748A5 (enrdf_load_html_response)
GB (1) GB1310288A (enrdf_load_html_response)
NL (1) NL7008933A (enrdf_load_html_response)
PL (1) PL81286B1 (enrdf_load_html_response)
RO (1) RO55423A (enrdf_load_html_response)
SE (1) SE349635B (enrdf_load_html_response)
SU (1) SU578018A3 (enrdf_load_html_response)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3759239A (en) * 1970-06-08 1973-09-18 Peugeot Injection devices for compression-ignited internal combustion engines
US3943901A (en) * 1973-02-19 1976-03-16 Diesel Kiki Kabushiki Kaisha Unit injector for a diesel engine
US4073275A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump
US4100903A (en) * 1976-12-13 1978-07-18 Stanadyne, Inc. Rotary distributor 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
US4291657A (en) * 1978-11-17 1981-09-29 Codrington Ernest R Diesel engine speed governor
US4345563A (en) * 1979-07-19 1982-08-24 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4348998A (en) * 1977-01-29 1982-09-14 Robert Bosch Gmbh Fuel injection pump
WO1982003890A1 (en) * 1981-05-04 1982-11-11 Richard A Cemenska Fuel injection system with rotor-filled pumping cavity
WO1982004287A1 (en) * 1981-05-26 1982-12-09 Alexander Goloff Rotary controlled fuel injection apparatus with automatic shut-off
US4380976A (en) * 1980-10-20 1983-04-26 Peter Bottiglieri Fuel flow arrestor
US4387686A (en) * 1981-01-27 1983-06-14 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
US4398518A (en) * 1980-01-12 1983-08-16 Robert-Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
US4407253A (en) * 1980-04-03 1983-10-04 Robert Bosch Gmbh Fuel injection pump for self-igniting internal combustion engines
US4445484A (en) * 1980-04-30 1984-05-01 Renault Vehicules Industriels Mechanical fuel injection devices, mainly for diesel engines
US4502445A (en) * 1982-04-19 1985-03-05 Spica, S.P.A. Delivery regulator for a fuel injection pump
US4526150A (en) * 1983-03-05 1985-07-02 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US4526149A (en) * 1983-03-05 1985-07-02 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US4530337A (en) * 1983-01-13 1985-07-23 Robert Bosch Gmbh Fuel injection pump
US5214122A (en) * 1992-07-13 1993-05-25 Eastman Kodak Company Preparation of multiply-branched cycloalkyl polyesters and multiply-branched cycloalkyl polyesters
US5225522A (en) * 1992-07-13 1993-07-06 Eastman Kodak Company Multiply-branched aliphatic-aromatic polyesters and method for preparing multiply-branched aliphatic-aromatic polyesters
US5227462A (en) * 1992-07-13 1993-07-13 Eastman Kodak Company Preparation of multiply-branched aliphatic-aromatic polyesters and multiply-branched aliphatic-aromatic polyesters
US6135073A (en) * 1999-04-23 2000-10-24 Caterpillar Inc. Hydraulic check valve recuperation

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3759239A (en) * 1970-06-08 1973-09-18 Peugeot Injection devices for compression-ignited internal combustion engines
US3943901A (en) * 1973-02-19 1976-03-16 Diesel Kiki Kabushiki Kaisha Unit injector for a diesel engine
US4073275A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump
US4100903A (en) * 1976-12-13 1978-07-18 Stanadyne, Inc. Rotary distributor fuel injection pump
US4348998A (en) * 1977-01-29 1982-09-14 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
US4291657A (en) * 1978-11-17 1981-09-29 Codrington Ernest R Diesel engine speed governor
US4345563A (en) * 1979-07-19 1982-08-24 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4398518A (en) * 1980-01-12 1983-08-16 Robert-Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
US4407253A (en) * 1980-04-03 1983-10-04 Robert Bosch Gmbh Fuel injection pump for self-igniting internal combustion engines
US4445484A (en) * 1980-04-30 1984-05-01 Renault Vehicules Industriels Mechanical fuel injection devices, mainly 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
US4380976A (en) * 1980-10-20 1983-04-26 Peter Bottiglieri Fuel flow arrestor
US4387686A (en) * 1981-01-27 1983-06-14 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines, in particular for diesel engines
WO1982003890A1 (en) * 1981-05-04 1982-11-11 Richard A Cemenska Fuel injection system with rotor-filled pumping cavity
WO1982004287A1 (en) * 1981-05-26 1982-12-09 Alexander Goloff Rotary controlled fuel injection apparatus with automatic shut-off
US4502445A (en) * 1982-04-19 1985-03-05 Spica, S.P.A. Delivery regulator for a fuel injection pump
US4530337A (en) * 1983-01-13 1985-07-23 Robert Bosch Gmbh Fuel injection pump
US4526150A (en) * 1983-03-05 1985-07-02 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US4526149A (en) * 1983-03-05 1985-07-02 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US5214122A (en) * 1992-07-13 1993-05-25 Eastman Kodak Company Preparation of multiply-branched cycloalkyl polyesters and multiply-branched cycloalkyl polyesters
US5225522A (en) * 1992-07-13 1993-07-06 Eastman Kodak Company Multiply-branched aliphatic-aromatic polyesters and method for preparing multiply-branched aliphatic-aromatic polyesters
US5227462A (en) * 1992-07-13 1993-07-13 Eastman Kodak Company Preparation of multiply-branched aliphatic-aromatic polyesters and multiply-branched aliphatic-aromatic polyesters
US6135073A (en) * 1999-04-23 2000-10-24 Caterpillar Inc. Hydraulic check valve recuperation

Also Published As

Publication number Publication date
JPS5323449B1 (enrdf_load_html_response) 1978-07-14
DE1931039A1 (de) 1971-01-07
GB1310288A (en) 1973-03-14
NL7008933A (enrdf_load_html_response) 1970-12-22
AT299625B (de) 1972-06-26
SU578018A3 (ru) 1977-10-25
PL81286B1 (enrdf_load_html_response) 1975-08-30
FR2052748A5 (enrdf_load_html_response) 1971-04-09
ES380887A1 (es) 1972-09-16
SE349635B (enrdf_load_html_response) 1972-10-02
RO55423A (enrdf_load_html_response) 1973-09-20
CH500377A (de) 1970-12-15

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