US3638626A - Engine spark timing control device - Google Patents

Engine spark timing control device Download PDF

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Publication number
US3638626A
US3638626A US52326A US3638626DA US3638626A US 3638626 A US3638626 A US 3638626A US 52326 A US52326 A US 52326A US 3638626D A US3638626D A US 3638626DA US 3638626 A US3638626 A US 3638626A
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United States
Prior art keywords
spark
servo
port
spark port
engine
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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
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US52326A
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English (en)
Inventor
John R Marshall
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Ford Motor Co
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Ford Motor Co
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Publication date
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Publication of US3638626A publication Critical patent/US3638626A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
    • F02P5/00—Advancing or retarding ignition; Control therefor
    • F02P5/04—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions
    • F02P5/05—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means
    • F02P5/10—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means dependent on fluid pressure in engine, e.g. combustion-air pressure
    • F02P5/103—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means dependent on fluid pressure in engine, e.g. combustion-air pressure dependent on the combustion-air pressure in engine

Definitions

  • An internal-combustion engine has a vacuum servo connected to the distributor breaker plate for moving it as a function of the change in carburetor spark port vacuum as controlled by a mechanical device between the servo and spark port having sintered metal flow restriction and a one-way check valve in parallel flow circuits, the check valve unseating during rapid vehicle accelerations to quickly reduce the spark advance setting to a lower level, for better performance, the sintered metal flow restriction providing a delayed rate of return to an advanced spark timing setting during relatively slower accelerations, to minimize the emission of undesirable exhaust gas elements.
  • This invention relates, in general, to a device that aids in the reduction of exhaust emission pollutants from an internalcombustion engine. More specifically, it relates to a mechanical spark timing control device that automatically varies the spark timing setting in accordance with changing engine conditions to provide engine performance, and yet minimize the output of undesirable elements.
  • vacuum servos automatically controlling the advance or retard setting of the engine distributor breaker plate as a function of carburetor spark port vacuum to provide good engine performance as well as fuel economy during the different operating conditions of the engine.
  • These vacuum servos in their simplest forms, generally consist of a housing divided into atmospheric pressure and vacuum chambers by a flexible diaphragm connected to the distributor breaker plate.
  • the diaphragm and breaker plate are normally spring biased to the lowest advance or retard spark timing setting, and carburetor spark port vacuum normally urges the diaphragm in a spark timing advance direction upon opening of the carburetor throttle valve in an engine speed increasing direction.
  • FIG. 1 illustrates schematically a cross-sectional view of an engine spark timing control apparatus embodying the invention
  • FlG. 2 illustrates a portion of the FIG. 1 showing in a different operative position.
  • FIG. 1 shows, schematically, only those portions of an internal-combustion engine that are normally associated with the engine distributor spark timing setting control; such as, for example, a carburetor 10, a distributor breaker plate 12, a vacuum servo 14 to control the movement of breaker plate 12, and a line 16 connected between the carburetor and vacuum servo to automatically change the engine spark timing setting as a function of changes in engine vacuum spark port setting.
  • a carburetor 10 a distributor breaker plate 12
  • a vacuum servo 14 to control the movement of breaker plate 12
  • line 16 connected between the carburetor and vacuum servo to automatically change the engine spark timing setting as a function of changes in engine vacuum spark port setting.
  • carburetor is shown as being of the downdraft type having the usual air-fuel induction passage 18 with an atmospheric air inlet 20 at one end and connected to the engine intake manifold 22 at the opposite end.
  • Passage 18 contains the usual fixed area venturi 24 and a throttle valve 26. The latter is rotatably mounted on a part of the carburetor body across passage 18 in a manner to control the flow of airfuel mixture into the intake manifold.
  • Fuel would be inducted in the usual manner from a nozzle, not shown, projecting into or adjacent venturi 24, in a known manner.
  • Throttle valve 26 is shown in its engine idle speed position essentially closing induction passage 18, and is rotatable to a nearly vertical position essentially unblocking passage 18.
  • a spark port 28 is provided at a point just above the idle position of throttle valve 26, to be traversed by the throttle valve during its opening or part throttle movements. This will change the vacuum level in spark port 28 as a function of the rotative position of the throttle valve, the spark port reflecting essentially atmospheric pressure in the air inlet 20 upon closure of the throttle valve.
  • the distributor includes a breaker plate 12 that is pivotally mounted at 30 on a stationary portion of the distributor, and movable with respect to cam 32.
  • the latter has six peaks 34 corresponding to the number of engine cylinders, each cooperating with the follower 36 of a breaker point set 38 to make and break the spark connection in a known manner for each one-sixth, in this case, rotation of cam 32.
  • Pivotal movement of breaker plate 12 in a counterclockwise spark retard setting direction, or in a clockwise spark advance setting is provided by an actuator 40 slidably extending from vacuum servo l4.
  • Servo 14 may be of a conventional construction. It has a hollow housing 42 whose interior is divided into an atmospheric pressure chamber 44 and a vacuum chamber 46 by an annular flexible diaphragm 48. The diaphragm is fixedly secured to actuator 40, and is biased in a rightward retard direction by a compression spring 50. Chamber 44 has an atmospheric or ambient pressure vent, not shown, while the chamber 46 is connected by a bore 52 to line 16.
  • the system includes a mechanical device 53 having an outer housing 54.
  • the latter has a connection 55 at one end to line 16, and a connection 56 at the opposite end to carburetor spark port 28.
  • Housing 54 is divided into two chambers 58 and 59 by an annular partition 60 having a number of radially spaced sets of circumferentially spaced apertures 61 and 62.
  • the apertures 62 are adapted to be controlled by a flexible one-way check valve 64.
  • Check valve 64 consists of a flapper or umbrella-typeseal having a flexible membrane 66 secured on an axial stem 68.
  • the stem projects through a central bore 70 in partition 58, and is fixed therein by means of spaced shoulders or flanges 72 and 74.
  • Membrane 66 is responsive to the differential in pressures on opposite sides thereof to move alternately to the positions shown'in FIGS. 1 and 2.
  • FIG. 1 the pressure level in the chamber 58 is greater than in the left hand chamber 59.
  • the membrane 66 In the open position shown in FIG. 2, the membrane 66 is flexed outwardly when the pressure level in chamber 59 is greater than in chamber 58; to permit a free communication through holes 62 between chambers.
  • Holes 61 contain sintered metal plugs 76 that each consist of randomly oriented and dispersed multitudes of minute metal particles compacted together under pressure into discs and passed through a furnace to bond the particles to each other. This defines a multitude of labyrinthian-type fluid passages connecting the voids between particles, and provides an extremely close tolerance flow restrictor or orifice.
  • particles may be balls, or free-shaped bent plate particles, for example. Their size will control the flow restriction.
  • An actual conventional orifice of such a small flow capacity could not feasibly be made under production conditions.
  • Such a small size orifice made in a conventional manner by providing merely a reduced diameter passage could easily be plugged by a small piece of dirt, whereas dust and grease will not clog up a sintered metal orifice of this type because of the multitude of differently oriented flow passages.
  • the sintered metal plugs therefore, constitute a flow restricting means that delays the communication between opposite sides of partition member 58 when the check valve 64 is closed.
  • the wall of housing 54 contains an atmospheric or ambient pressure air bleed consisting of a sintered metal plug 78.
  • the latter is similar in construction to plugs 76, but of a larger flow area; i.e., less restriction.
  • the air bleed assures a flow through the line 80 at all times, when the throttle valve is open, in a direction from the chamber 59 to spark port 28, to prevent fuel leakage from the carburetor entering line 80 and contaminating the check valve membrane 66 or servo diaphragm 48. That is, during part throttle operation, the vacuum in line 80 pulls air through the bleed 78 at the same time flow is through the sintered plugs 76, since chamber 58 is at a higher absolute pressure level.
  • Flow through the bleed 78 does not appreciably affect the flow through plugs 76, however, since the engine has an airflow capacity far in excess of what normally flows through the sintered plugs 76 alone. Therefore, any fuel that might tend to leak into line 80 is purged by the airflow from bleed 78.
  • engine spark port 28 will be at atmospheric pressure, as will both chambers 44 and 46 of the servo 14. Therefore, the distributor breaker plate 12 will be placed in its lowest engine spark timing advance or a retard position by servo spring 50.
  • the vehicle throttle valve 26 now were permitted to return towards or to its idle speed position, from the rapid acceleration position previously attained, the vehicle then begins driving the engine, and the spark port vacuum immediately decays to a lower value that normally will be a higher absolute pressure than previous and higher than in the servo chamber 48. This immediately pops off the seated check valve 64 and permits a quick equalization of the vacuum servo chamber 48 pressure to that of the spark port pressure level to reduce the advance setting of the distributor to a lower engine operating setting. Once the pressure levels are equalized, the check valve or flapper valve 64 again will seat.
  • the invention provides an engine spark timing control that immediately and automatically provides the desired spark timing setting for engine performance, and yet reduces the output of undesirable exhaust pollutants by delaying normal advance timing during gradual part throttle engine accelerating conditions of opera tion.
  • a spark timing control system comprising, an engine carburetor having an induction passage containing a spark port located above the idle speed position of a throttle valve controlling flow through the passage and subject to the depression in the carburetor as a function of the movement of the throttle valve from its idle speed position, an engine distributor having a breaker plate pivotally movable in opposite directions to advance and retard the spark timing, vacuum controlled servo means connected to said breaker plate for moving the same, and slow-fast flow rate control means between said spark port and servo means to control the rate of change of application of vacuum from said spark port to said servo means, said control means including faster flow rate means operable in response to a change in the depression at said spark port to a lesser depression than at said servo means to quickly equalize the pressure level at said servo means to that at the spark port, and slower flow rate means operable in response to a change in the depression at said spark port to a greater depression than at the servo means to delay the equalization of the pressure level at the servo means to
  • control means including a conduit means between said spark port and servo means containing said faster flow rate means, the latter comprising a one-way check valve.
  • control means including a conduit means connecting said spark port to said servo means and containing said slower flow rate means, the latter comprising flow restricting means.
  • control means including a conduit connecting said spark port vacuum to said servo means, said conduit containing flow restricting orifice means constituting said slower rate flow means, said conduit having a bypass branch around said orifice means containing a one-way check valve constituting said faster flow rate means.
  • a spark timing control system comprising an engine carburetor having an induction passage containing a spark port located above the idle speed position of a throttle valve controlling flow through the passage and subject to the depression in the carburetor as a function of the movement of the throttle valve from its idle speed position, an engine distributor having a breaker plate pivotally movable in opposite directions to advance and retard the spark timing, vacuum controlled servo means connected to said breaker plate for moving the same, a conduit connecting said spark port to said servo means, and a plurality of flow rate control means in said conduit means, said control means including one-way check valve means in said conduit operable upon acceleration of said engine by movement of said throttle valve from its idle speed position increasing the pressure level in said spark port to quickly equalize the pressure level at the servo means to that at the spark port to thereby move the breaker plate from its initially higher to a lower spark timing advance setting, said conduit means also i t l

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Electrical Control Of Ignition Timing (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
US52326A 1970-07-06 1970-07-06 Engine spark timing control device Expired - Lifetime US3638626A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US5232670A 1970-07-06 1970-07-06

Publications (1)

Publication Number Publication Date
US3638626A true US3638626A (en) 1972-02-01

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US52326A Expired - Lifetime US3638626A (en) 1970-07-06 1970-07-06 Engine spark timing control device

Country Status (6)

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US (1) US3638626A (de)
JP (1) JPS5235828B1 (de)
CA (1) CA935342A (de)
DE (1) DE2133313C2 (de)
FR (1) FR2100253A5 (de)
GB (1) GB1293288A (de)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3730154A (en) * 1972-02-02 1973-05-01 Ford Motor Co Engine spark timing control
US3857373A (en) * 1972-12-01 1974-12-31 Chrysler Corp Vacuum delay valve
US3911880A (en) * 1973-10-30 1975-10-14 Ford Motor Co Spark delay device for internal combustion engine ignition timing
DE2635726A1 (de) * 1975-08-11 1977-02-17 Honda Motor Co Ltd Fahrzeug-brennkraftmaschine
US4040401A (en) * 1974-11-05 1977-08-09 Ethyl Corporation Spark vacuum advance control
US4068634A (en) * 1974-08-08 1978-01-17 Honda Giken Kogyo Kabushiki Kaisha Control system for ignition timing of engine
US4091778A (en) * 1975-07-11 1978-05-30 Toyota Jidosha Kogyo Kabushiki Kaisha Vacuum advancer system for a gasoline engine
US4098850A (en) * 1974-09-04 1978-07-04 Aisin Seiki Kabushiki Kaisha Orifice device for air flow restriction
US4098245A (en) * 1976-03-16 1978-07-04 Toyota Jidosha Kogyo Kabushiki Kaisha Apparatus for controlling the ignition timing of an internal combustion engine
US4126084A (en) * 1973-10-11 1978-11-21 Masami Inada Ignition time adjuster for an internal combustion engine
US4241751A (en) * 1976-05-07 1980-12-30 Toyota Jidosha Kogyo Kabushiki Kaisha Vacuum transmitting valve
US4267809A (en) * 1978-07-05 1981-05-19 Nissan Motor Company, Limited Exhaust gas recirculation control system
DE3325161A1 (de) * 1982-07-12 1984-02-02 Schmelzer Corp., 48507 Flint, Mich. Druckempfindliche ventilanordnung
US4796585A (en) * 1985-10-31 1989-01-10 Kim Sang H Vacuum advance regulator for a spark ignition engine
US5606947A (en) * 1995-03-29 1997-03-04 Hong; Fu C. Automotive acceleration-horsepower control means
US20180100600A1 (en) * 2016-10-11 2018-04-12 Honda Motor Co., Ltd. Control valve unit
US20210324969A1 (en) * 2017-03-30 2021-10-21 Donaldson Company, Inc. Vent with relief valve
US11796076B1 (en) 2022-05-09 2023-10-24 Vernay Laboratories, Inc. Pressure accomodating assembly

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3678907A (en) * 1970-07-30 1972-07-25 Ford Motor Co Engine spark timing system
DE2812291C3 (de) * 1978-03-21 1994-07-07 Bosch Gmbh Robert Zündanlage für Brennkraftmaschinen
JPS55162642U (de) * 1979-05-10 1980-11-21
JPS55162644U (de) * 1979-05-10 1980-11-21
JPS5744837U (de) * 1980-08-25 1982-03-12
US4986310A (en) * 1990-01-22 1991-01-22 Vernay Laboratories, Inc. Low pressure check valve

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2650581A (en) * 1949-11-03 1953-09-01 Gen Motors Corp Ignition apparatus
US3476094A (en) * 1968-03-13 1969-11-04 Gen Motors Corp Internal combustion engine ignition spark vacuum advance mechanism delay system

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3131681A (en) * 1962-03-09 1964-05-05 Ford Motor Co Spark advance system

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2650581A (en) * 1949-11-03 1953-09-01 Gen Motors Corp Ignition apparatus
US3476094A (en) * 1968-03-13 1969-11-04 Gen Motors Corp Internal combustion engine ignition spark vacuum advance mechanism delay system

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3730154A (en) * 1972-02-02 1973-05-01 Ford Motor Co Engine spark timing control
US3857373A (en) * 1972-12-01 1974-12-31 Chrysler Corp Vacuum delay valve
US4126084A (en) * 1973-10-11 1978-11-21 Masami Inada Ignition time adjuster for an internal combustion engine
US3911880A (en) * 1973-10-30 1975-10-14 Ford Motor Co Spark delay device for internal combustion engine ignition timing
US4068634A (en) * 1974-08-08 1978-01-17 Honda Giken Kogyo Kabushiki Kaisha Control system for ignition timing of engine
US4098850A (en) * 1974-09-04 1978-07-04 Aisin Seiki Kabushiki Kaisha Orifice device for air flow restriction
US4040401A (en) * 1974-11-05 1977-08-09 Ethyl Corporation Spark vacuum advance control
US4091778A (en) * 1975-07-11 1978-05-30 Toyota Jidosha Kogyo Kabushiki Kaisha Vacuum advancer system for a gasoline engine
DE2635726A1 (de) * 1975-08-11 1977-02-17 Honda Motor Co Ltd Fahrzeug-brennkraftmaschine
US4098245A (en) * 1976-03-16 1978-07-04 Toyota Jidosha Kogyo Kabushiki Kaisha Apparatus for controlling the ignition timing of an internal combustion engine
US4241751A (en) * 1976-05-07 1980-12-30 Toyota Jidosha Kogyo Kabushiki Kaisha Vacuum transmitting valve
US4267809A (en) * 1978-07-05 1981-05-19 Nissan Motor Company, Limited Exhaust gas recirculation control system
DE3325161A1 (de) * 1982-07-12 1984-02-02 Schmelzer Corp., 48507 Flint, Mich. Druckempfindliche ventilanordnung
US4796585A (en) * 1985-10-31 1989-01-10 Kim Sang H Vacuum advance regulator for a spark ignition engine
US5606947A (en) * 1995-03-29 1997-03-04 Hong; Fu C. Automotive acceleration-horsepower control means
US20180100600A1 (en) * 2016-10-11 2018-04-12 Honda Motor Co., Ltd. Control valve unit
US10415716B2 (en) * 2016-10-11 2019-09-17 Honda Motor Co., Ltd. Control valve unit
US20210324969A1 (en) * 2017-03-30 2021-10-21 Donaldson Company, Inc. Vent with relief valve
US11692644B2 (en) * 2017-03-30 2023-07-04 Donaldson Company, Inc. Vent with relief valve
US12078265B2 (en) 2017-03-30 2024-09-03 Donaldson Company, Inc. Vent with relief valve
US11796076B1 (en) 2022-05-09 2023-10-24 Vernay Laboratories, Inc. Pressure accomodating assembly

Also Published As

Publication number Publication date
DE2133313C2 (de) 1982-09-23
GB1293288A (en) 1972-10-18
JPS5235828B1 (de) 1977-09-12
FR2100253A5 (de) 1972-03-17
CA935342A (en) 1973-10-16
DE2133313A1 (de) 1972-01-13

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